CN1220012C - Refrigerating circulation apparatus - Google Patents

Refrigerating circulation apparatus Download PDF

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Publication number
CN1220012C
CN1220012C CNB03136067XA CN03136067A CN1220012C CN 1220012 C CN1220012 C CN 1220012C CN B03136067X A CNB03136067X A CN B03136067XA CN 03136067 A CN03136067 A CN 03136067A CN 1220012 C CN1220012 C CN 1220012C
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CN
China
Prior art keywords
mentioned
cold
producing medium
temperature
linearkompressor
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Expired - Fee Related
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CNB03136067XA
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Chinese (zh)
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CN1455214A (en
Inventor
植田光男
吉田诚
药丸雄一
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Panasonic Holdings Corp
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Matsushita Electric Industrial Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/073—Linear compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

The object of the invention is to safely and stably control the refrigerating capability of a refrigerating cycle device having a linear compressor 1a according to load. This device has a volume circulating quantity instruction part 7 for determining the volume circulating quantity of coolant Vco according to the refrigerating capability required for the refrigerating cycle device 101 based on the peripheral temperature of an indoor heat exchanger (evaporator) 53a, a target temperature set by a user to the evaporator 53a, and the circumferential temperature of an outdoor heat exchanger (condenser) 55; a volume circulating quantity detection part 8a for detecting the volume circulating quantity of coolant Vcd actually carried in the coolant circulating route of the refrigerating cycle device 101; and an inverter 2 for generating AC current for driving the linear compressor 1a. The inverter 2 is controlled so as to reduce the difference between the volume circulating quantity of coolant Vco and the volume circulating quantity of coolant Vcd.

Description

Refrigerating circulatory device
Technical field
The present invention relates to refrigerating circulatory device, in particular, the present invention relates to following refrigerating circulatory device, this refrigerating circulatory device adopts by linear motor and makes reciprocating motion of the pistons in the cylinder, produces the Linearkompressor of the Compressed Gas of cold-producing medium.
Background technology
In the past, as the equipment of the Compressed Gas that produces cold-producing medium, people know the elastomeric element that adopts machinery, or utilizes the refrigerating circulatory device of the flexible Linearkompressor of Compressed Gas.As the concrete example that is fit to of such refrigerating circulatory device, people consider to have to carry out indoor refrigeration and heating, and room temperature is remained on the air conditioner of comfortable temperature, and freezing by in the case will remain on the fridge-freezer etc. of suitable low-temperature condition in the case.
Figure 11 is used to illustrate the figure that is used for Linearkompressor such refrigerating circulatory device, elastomeric element employing spring.
Linearkompressor 1 comprises along the axis 71a of cylinder body portion side by side of regulation, and motor part 71b.Inside at the 71a of this cylinder body portion is provided with the piston 72 that supports slidably along above-mentioned axis direction.Be provided with the piston rod 72a that the one end is fixed in the rear side of piston 72 in the inside of cylinder body 71, at another distolateral support spring (resonant spring) 81 that is provided with of piston rod 72a, this spring 81 is along this piston rod of axis direction bias voltage 72a.
In addition, on above-mentioned piston rod 72a magnet 73 is installed, on the part in above-mentioned motor part 71b, that face with magnet 73 electromagnet 74 is installed, this electromagnet 74 is made of outside yoke (york) 74a and stator coil 74b of being embedded in it.In above-mentioned Linearkompressor 1, constitute linear motor 82 by electromagnet 74 and magnet 73, this magnet 73 is installed on the above-mentioned piston rod, and by the electromagnetic force of generation between electromagnet 74 and magnet 73 and the elastic force of above-mentioned spring 81, above-mentioned piston 72 moves back and forth along axis direction.
In addition, be formed with as by cylinder top underside 75 piston compressing surface 72b, and the discharge chambe 76 of the seal cavity that centers on of cylinder peripheral wall surfaces 71a1 in the inside of the 71a of cylinder body portion.On cylinder top underside 75, suck the end opening of the gas side suction line 1a that low pressure refrigerant gas use towards discharge chambe 76 from the gas side flow passage, in addition, on above-mentioned cylinder top underside 75, be used for discharging towards the gas side flow passage end opening of the discharge pipe 1b of used for high-pressure refrigerant from above-mentioned discharge chambe 76.At the end of above-mentioned suction line 1a and discharge pipe 1b, the inlet valve 79 and the dump valve 80 of the adverse current that prevents refrigerant gas is installed.
Also have, in Linearkompressor 1, feed drive current by drive circuit (not shown) to this linear motor 82 from above-mentioned linear motor 82, piston 72 moves back and forth along axis direction, carries out repeatedly towards the discharge from discharge chambe 76 of the suction of the low pressure refrigerant gas of discharge chambe 76, the compression of refrigerant gas in the discharge chambe 76 and the high pressure refrigerant gas that has been compressed.
Have again,, implement following method widely, in the method,, the running of the compressor of formation refrigerating circulatory device is controlled with feedback system according to the thermic load state of refrigerating circulatory device as the method for control refrigerating circulatory device.
Figure 12 is the figure that is used to illustrate a suitable example of refrigerating circulatory device, the air conditioner that its expression is cooling.
This air conditioner (refrigerating circulatory device) 50 comprises: indoor set 51, this indoor set 51 are arranged at the inside (indoor) in room, freeze to indoor; Off-premises station 52, this off-premises station 52 are arranged at the outside (outdoor) in room, waste heat.
Above-mentioned indoor set 51 comprises: indoor heat converter (evaporimeter) 53, and this indoor heat converter 53 carries out heat exchange between indoor air and cold-producing medium, from indoor absorption of air heat; Room temperature detector 54, this room temperature detector 54 detect the temperature that is drawn into the air in this evaporimeter 53, are room temperature (peripheral temperature of evaporimeter).
Off-premises station 52 comprises: outdoor heat converter (condenser) 55, and the heat exchange that this outdoor heat converter 55 carries out between extraneous gas and the cold-producing medium is to the extraneous gas discharges heat; Compressor 56, this compressor 56 is arranged at cold-producing medium is flowed to from evaporimeter 53 on the part of gas side flow passage Gp of condenser 35, refrigerant gas from evaporimeter 53 suction low-temp low-pressures compresses it, and the refrigerant gas of HTHP is sent to condenser 55.In addition, off-premises station 52 comprises expansion valve 57, this expansion valve 57 is configured in cold-producing medium is flowed to from condenser 55 on the part of liquid side flow path Lp of evaporimeter 53, and the liquid refrigerant of high pressure is reduced to the liquid refrigerant of low pressure, makes cold-producing medium with lower temperature evaporation.In addition, in Figure 12, Lmf is illustrated in the direction of hydraulic fluid side flow passage Lp internal refrigeration storage liquid flow, and Gmf is illustrated in the direction of the internal refrigeration storage gas flow of gas side flow passage Gp.
Here, the effect of above-mentioned condenser 55 and evaporimeter 53 is simply described.
In condenser 55, in the air drawn that the heat of the refrigerant gas of the HTHP of internal flow is admitted to, this refrigerant gas liquefies gradually, forms the liquid refrigerant of high pressure near the outlet of condenser 55.This is equivalent to cold-producing medium discharges heat in atmosphere, realizes liquefaction.
In addition, the liquid refrigerant that becomes the low-temp low-pressure state by expansion valve 57 flow in this evaporimeter 53.If the air with the room under this state is sent in the evaporimeter 53, then liquid refrigerant evaporates from a large amount of heat of air drawn, becomes the gas refrigerant of low-temp low-pressure.Drawn the inflatable mouth formation cold wind of the air of a large amount of heat by evaporimeter 53, discharged from air conditioner.
As above-mentioned, in above-mentioned air conditioner 50, the circulation that is formed cold-producing medium by evaporimeter 53, condenser 55, gas side flow passage Gp and the hydraulic fluid side flow passage Lp between them, the expansion valve 57 that is arranged at the compressor 56 of gas side flow passage Gp and is arranged at hydraulic fluid side flow passage Lp is closed circuit, make by compressor 56 and to be encapsulated in the cold-producing medium circulation of this circulation in closed circuit, thus, form known heat pump cycle in the closed circuit inside of the circulation of cold-producing medium.
Here, as the mode of internal circulating load of control cold-producing medium, generally be adopt above-mentioned relatively air conditioner and the method for the target temperature set and actual room temperature (such as, with reference to patent documentation 1).
Figure 13 is the figure of freeze cycle control method that is used to illustrate the past of the cooling air conditioner of control.
In the freeze cycle control method in this past, detect by indoor device suction temperature detector 60 by the indoor temperature (room temperature) of air conditioner refrigeration.The concrete detection method of room temperature considers that following method is arranged, in method, and the temperature of the temperature sensor measurement room air of employing thermocouple etc.In addition, in room temperature setting apparatus 61,, the desirable indoor temperature of user is set at target temperature according to user's operation signal.In the concrete establishing method of this target temperature, people consider to adopt following method, in the method, by microprocessor the operation signal from the remote controller of air conditioner are handled, and it is calculated.In addition, by subtraction exerciser 63 calculating indoor set suction temperature detector 60 detected indoor temperature Tdet with by the temperature difference Tdiff between the target temperature Tord of room temperature setting apparatus 61 settings.In compressor revolution instruction device 62, send instruction to compressor, so that the rotational speed omega ord of compressor 56 becomes the rotating speed of corresponding said temperature difference Tdiff.Specifically, said temperature difference Tdiff is big more, and compressor rotary speed ω ord is big more.
[patent documentation 1]
The flat 9-68341 communique of TOHKEMY.
The problem that the present invention will solve
But, in the freeze cycle control method in above-mentioned past, poor corresponding to the temperature in the room that freezes and target temperature, change the rotating speed of compressor, the internal circulating load of the cold-producing medium that circulates in freeze cycle is defined as in the refrigerating circulatory device of certain value by the rotating speed of compressor, can carry out freeze cycle control efficiently, yet, in the refrigerating circulatory device that the internal circulating load of cold-producing medium is not only determined by the rotating speed of compressor, has the problem that is difficult to carry out high efficiency freeze cycle control.
Such as, at the compressor (revolution type compressor) that adopts rotary-type motor in the past, specifically, in reciprocating compressor, rotary compressor, vortex (scroll) compressor etc., determine to follow motor to revolve and turn around and the volume of compressed cold-producing medium.Thus, in adopting the refrigerating circulatory device of revolution type compressor, the internal circulating load of the cold-producing medium that will be circulated in freeze cycle by the motor speed of this compressor is determined at certain value.Thus, in revolution type compressor, control, can carry out high efficiency freeze cycle control by rotating speed to compressor.
On the other hand, in the refrigerating circulatory device that adopts the such Linearkompressor of foregoing description, because the volume-variation of the discharge chambe of compressor, so do not determined by a meaning by the volume of primary coolant compressed action refrigerant compressed.In addition, in the refrigerating circulatory device that adopts Linearkompressor, not certain, so can't calculate the internal circulating load of the cold-producing medium in the freeze cycle according to the stroke of piston owing to when compressed action finishes, residue in the amount of the cold-producing medium in the discharge chambe yet.Consequently, in adopting the refrigerating circulatory device of Linearkompressor,, that is, control, can't carry out high efficiency freeze cycle control by reciprocating motion number of times to the piston of unit interval by the rotating speed control of compressor.
Summary of the invention
The present invention proposes in order to solve above-mentioned such problem, the objective of the invention is to obtain following refrigerating circulatory device, this refrigerating circulatory device can be controlled refrigerating capacity expeditiously corresponding to the temperature and the temperature difference between the target temperature of the reality in the room that freezes or heat etc., and this refrigerating circulatory device adopts Linearkompressor.
Refrigerating circulatory device of the present invention comprises: the 1st heat exchanger and the 2nd heat exchanger that form the peripheral passage of cold-producing medium; Linearkompressor, this Linearkompressor has piston and makes the linear motor of this reciprocating motion of the pistons, follow the reciprocating motion of this piston that the cold-producing medium in the above-mentioned peripheral passage is circulated, it is characterized in that this refrigerating circulatory device comprises: reverser, this reverser produces the alternating current that drives above-mentioned linear motor; Actual cycle amount test section, this actual cycle amount test section detects the reciprocating motion that above-mentioned piston is followed in expression, the circulating mass of refrigerant of the reality of the volume of the cold-producing medium that the Linearkompressor unit interval discharges or sucks; Target circulation amount leading-out portion, the target temperature that this target circulation amount leading-out portion is set according to both sides in above-mentioned the 1st heat exchanger and the 2nd heat exchanger or a side's peripheral temperature and a side in relative at least this two heat-exchanger, the target circulating mass of refrigerant of the volume of the cold-producing medium that the above-mentioned Linearkompressor unit interval of induced representation should be discharged or suck; Control part, this control part is controlled above-mentioned reverser, makes the circulating mass of refrigerant of above-mentioned reality and the difference between the above-mentioned target circulating mass of refrigerant reduce.
The present invention is characterized in that it comprises in above-mentioned refrigerating circulatory device: stroke detection portion, and the trip test section detects the haul distance of the piston that moves back and forth; The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth, above-mentioned actual cycle amount test section calculates the volume that 1 time of following piston moves back and forth the cold-producing medium of discharging or sucking according to above-mentioned detected haul distance and above-mentioned detected upper dead center position, by the multiplying of the frequency of the alternating current that above-mentioned calculated volume and above-mentioned reverser produced, obtain the circulating mass of refrigerant of above-mentioned reality.
The present invention is in above-mentioned refrigerating circulatory device, it is characterized in that it comprises: discharge pressure is inferred portion, and this discharge pressure is inferred the pressure of portion according to the cold-producing medium of the above-mentioned Linearkompressor discharge of temperature estimation of the cold-producing medium of the heat exchanger that makes condensation of refrigerant of cold-producing medium discharge side in the above-mentioned peripheral passage, that be positioned at Linearkompressor; Suction pressure is inferred portion, this suction pressure is inferred portion according in the above-mentioned peripheral passage, be positioned at the pressure of the cold-producing medium that the above-mentioned Linearkompressor of temperature estimation of cold-producing medium of the heat exchanger that makes cold-producing medium evaporation of the cold-producing medium suction side of Linearkompressor sucks, the maximum pressure of the cold-producing medium of the above-mentioned peripheral passage that above-mentioned actual cycle amount test section obtains according to the pressure of the pressure of above-mentioned suction cold-producing medium of having inferred and the discharging refrigerant of having inferred by employing and the pressure ratio of minimum pressure, and the volume of obtaining the cold-producing medium of discharging or sucking according to the computing of above-mentioned detected haul distance and above-mentioned detected upper dead center position by 1 reciprocating motion of above-mentioned piston.
Refrigerating circulatory device of the present invention, this refrigerating circulatory device comprises: the 1st heat exchanger and the 2nd heat exchanger that form the peripheral passage of cold-producing medium; Linearkompressor, this Linearkompressor has piston and makes the linear motor of this reciprocating motion of the pistons, reciprocating motion by this piston circulates the cold-producing medium in the above-mentioned peripheral passage, it is characterized in that this refrigerating circulatory device comprises: reverser, this reverser produces the alternating current that drives above-mentioned linear motor; Actual cycle amount test section, this actual cycle amount test section detects the reciprocating motion that above-mentioned piston is followed in expression, the circulating mass of refrigerant of the reality of the weight of the cold-producing medium that the Linearkompressor unit interval discharges or sucks; The target circulating mass of refrigerant of the weight of the cold-producing medium that target circulation amount leading-out portion, this target circulation amount leading-out portion should be discharged or suck according to both sides in above-mentioned the 1st heat exchanger and the 2nd heat exchanger or a side's peripheral temperature and a target temperature induced representation above-mentioned Linearkompressor unit interval of setting in relative at least these two heat exchangers; Control part, this control part is controlled above-mentioned reverser, makes the circulating mass of refrigerant of above-mentioned reality and the difference between the above-mentioned target circulation amount reduce.
The present invention is characterized in that it comprises in above-mentioned refrigerating circulatory device: stroke detection portion, and the trip test section detects the haul distance of the piston that moves back and forth; The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth; Discharging refrigerant Density Detection portion, this discharging refrigerant Density Detection portion is detected from the density of the cold-producing medium of above-mentioned Linearkompressor discharge, above-mentioned actual cycle amount test section calculates the volume that by above-mentioned piston 1 time moves back and forth the cold-producing medium of discharging according to above-mentioned detected haul distance and above-mentioned detected upper dead center position, obtains the weight of the cold-producing medium that the unit interval discharges from Linearkompressor according to the frequency of this volume that calculates, above-mentioned detected density, alternating current that above-mentioned reverser produced
The present invention is characterized in that it comprises in above-mentioned refrigerating circulatory device: discharge temperature test section, this discharge temperature test section detect from the temperature of the cold-producing medium of above-mentioned Linearkompressor discharge; The discharge pressure test section, this discharge pressure test section detects the pressure of the cold-producing medium of discharging from above-mentioned Linearkompressor, and above-mentioned discharging refrigerant Density Detection portion derives from the density of the cold-producing medium of above-mentioned Linearkompressor discharge with pressure according to the temperature of above-mentioned detected cold-producing medium of discharging from Linearkompressor.
The present invention is characterized in that it comprises in above-mentioned refrigerating circulatory device: stroke detection portion, and the trip test section detects the haul distance of the piston that moves back and forth; The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth; Suck the refrigerant density test section, this suction refrigerant density test section detects the density that is drawn into the cold-producing medium in the above-mentioned Linearkompressor, above-mentioned actual cycle amount test section calculates the volume that by above-mentioned piston 1 time moves back and forth the cold-producing medium that sucks according to above-mentioned detected haul distance and above-mentioned detected upper dead center position, obtains the weight that the unit interval is drawn into the cold-producing medium in the Linearkompressor according to the density of this volume that has calculated, above-mentioned detected cold-producing medium and the frequency of the alternating current that above-mentioned reverser produced.
The present invention is characterized in that it comprises in above-mentioned refrigerating circulatory device: the inlet temperature test section, and this inlet temperature test section detects the temperature that is drawn into the cold-producing medium in the above-mentioned Linearkompressor; The suction pressure test section, this suction pressure test section detects the pressure that is drawn into the cold-producing medium in the above-mentioned Linearkompressor; Above-mentioned suction refrigerant density test section is obtained the density that is drawn into the cold-producing medium in the above-mentioned Linearkompressor according to the above-mentioned detected temperature and pressure that is drawn into the cold-producing medium in the Linearkompressor.
The present invention is in above-mentioned refrigerating circulatory device, it is characterized in that it comprises the refrigerant temperature detector, this refrigerant temperature detector detects the temperature as the cold-producing medium of the evaporimeter of heat exchanger that makes cold-producing medium evaporation of the cold-producing medium suction side that is positioned at Linearkompressor in the above-mentioned peripheral passage as the saturation temperature that is drawn into the cold-producing medium in the above-mentioned Linearkompressor; The degree of superheat is inferred portion, and this degree of superheat is inferred portion and inferred the degree of superheat as the cold-producing medium of the temperature difference that is drawn into the temperature of the cold-producing medium in the above-mentioned Linearkompressor and saturation temperature according to the operating condition of above-mentioned Linearkompressor; Above-mentioned inlet temperature test section carries out the addition calculation to the temperature of the cold-producing medium in the above-mentioned detected evaporimeter and the degree of superheat of above-mentioned cold-producing medium of having inferred, obtains the temperature that sucks the cold-producing medium in the above-mentioned Linearkompressor.
The present invention relates to a kind of air conditioner, this air conditioner comprises above-mentioned refrigerating circulatory device, it is characterized in that above-mentioned the 1st heat exchanger is an outdoor heat exchanger, and above-mentioned the 2nd heat exchanger is an indoor side heat exchanger.
The present invention relates to a kind of refrigerating box, this refrigerating box comprises above-mentioned refrigerating circulatory device, it is characterized in that above-mentioned the 1st heat exchanger is the condenser of discharges heat; Above-mentioned the 2nd heat exchanger is the evaporimeter to cooling off in the case.
The present invention relates to a kind of hot water supply apparatus, this hot water supply apparatus comprises above-mentioned refrigerating circulatory device, it is characterized in that the hopper that it comprises storage of water; The water heat exchanger that above-mentioned the 1st heat exchanger heats for the water to above-mentioned hopper; Above-mentioned the 2nd heat exchanger is the air heat exchanger that absorbs heat from peripheral atmosphere.
The present invention relates to a kind of utmost point low-temperature freezing facilities, this cryogenic refrigerator comprises above-mentioned refrigerating circulatory device, it is characterized in that it comprises refrigerating chamber, above-mentioned the 1st heat exchanger is the radiator of discharges heat, and above-mentioned the 2nd heat exchanger is the regenerator to cooling off in the above-mentioned refrigerating chamber.
Description of drawings
Fig. 1 is the block diagram that is used to illustrate the refrigerating circulatory device of the 1st embodiment of the present invention;
Fig. 2 is the block diagram that is used to illustrate the refrigerating circulatory device of the 2nd embodiment of the present invention;
Fig. 3 for explanation in the refrigerating circulatory device of above-mentioned the 2nd embodiment, according to the upper dead center position of the piston in the Linearkompressor figure with the method for stroke calculating circulating mass of refrigerant;
Fig. 4 is the block diagram that is used to illustrate the refrigerating circulatory device of the 3rd embodiment of the present invention;
Fig. 5 is the block diagram that is used to illustrate the refrigerating circulatory device of the 4th embodiment of the present invention;
Fig. 6 is the block diagram that is used to illustrate the refrigerating circulatory device of the 5th embodiment of the present invention;
Fig. 7 is the schematic diagram of the air conditioner of expression the 6th embodiment of the present invention;
Fig. 8 is the schematic diagram of the refrigerating box of expression the 7th embodiment of the present invention;
Fig. 9 is the schematic diagram of the hot water supply apparatus of expression the 8th embodiment of the present invention;
Figure 10 is the schematic diagram that is used to represent the utmost point low-temperature freezing facilities of the 9th embodiment of the present invention;
Figure 11 is the cutaway view that is used to represent Linearkompressor in the past;
Figure 12 is the system diagram that is used to illustrate general refrigerating circulatory device;
Figure 13 is the block diagram that is used to illustrate the system that the refrigerating capacity of the refrigerating circulatory device that adopts Linearkompressor is in the past controlled.
The specific embodiment
Below, with reference to the description of drawings embodiments of the present invention.
Refrigerating circulatory device of the present invention uses the device of Linearkompressor as circulating refrigerant, feature of the present invention is the internal circulating load that calculates the cold-producing medium in the refrigerating circulatory device according to the action of Linearkompressor piston, be volume in the Linearkompressor cold-producing medium time per unit of discharging or sucking or weight (below be also referred to as volume internal circulating load or weight internal circulating load), by driving the control Linearkompressor, the volume or the weight of feasible cold-producing medium of calculating become the value that is equivalent to desired refrigerating capacity, thereby refrigerating circulatory device is carried out at a high speed and stable control.
Here, the control of above-mentioned Linearkompressor is to be undertaken by the drive current that control is applied on the linear motor, in addition, the concrete control method of drive current can adopt the parameters such as amplitude, frequency or waveform of change drive current, make to reduce the method for the temperature difference of the temperature of surroundings of the condenser of refrigerating circulatory device and evaporimeter etc. and design temperature that this heat exchange is set.
(the 1st embodiment)
Fig. 1 is the figure that is used to illustrate the refrigerating circulatory device of the 1st embodiment of the present invention.
The refrigerating circulatory device 101 of the 1st embodiment of the present invention is for carrying out the air conditioner of indoor refrigeration, identical with the air conditioner 50 in past shown in Figure 8, comprising: the 1st heat exchanger (evaporimeter) 53a and the 2nd heat exchanger (condenser) 55a that form the peripheral passage (freeze cycle) of cold-producing medium; Linearkompressor 1a, this Linearkompressor 1a are arranged at the gas side circulation flow path Gp that connects above-mentioned two heat exchangers; Flow controller 57a, this flow controller 57a are provided with the hydraulic fluid side flow passage Lp that connects these two heat exchangers.
Here, above-mentioned Linearkompressor 1a is identical with Linearkompressor 1 shown in Figure 7, it comprises 71a of cylinder portion and the motor part 71b with piston 72, this motor part 71b comprises the linear motor 82 that makes these piston 72 reciprocating actions, this Linearkompressor circulates cold-producing medium by the reciprocating motion of piston in the peripheral passage of above-mentioned cold-producing medium.
In addition, above-mentioned refrigerating circulatory device 101 comprises the 101a of driven compressor portion, and the 101a of this driven compressor portion supplies with drive current Cd to the linear motor of above-mentioned Linearkompressor 1a, drives Linearkompressor 1a.
Below the 101a of this driven compressor portion is specifically described.
The 101a of this driven compressor portion comprises Temperature Detector 3 and 5, and this Temperature Detector 3 and 5 is used to detect the load condition of this refrigerating circulatory device 101.This Temperature Detector 3 is the 2nd surroundings Temperature Detector, and it detects temperature (environment temperature) THd of atmosphere of the periphery of above-mentioned the 2nd heat exchanger (condenser) 55a, the detection signal of the output detected temperature of expression (detected temperatures).Said temperature detector 5 is the 1st surroundings Temperature Detector, and it detects temperature (environment temperature) TLd of atmosphere of the periphery of above-mentioned the 1st heat exchanger (evaporimeter) 53a, the detection signal of the output detected temperature of expression (detected temperatures).
In addition, if said temperature detector 3 and 5 detects the environment temperature of heat exchanger, output temperature information then can be any type.Such as, for such Temperature Detector, exemplify the electrodynamic type thermometer that adopts bimetallic mechanical type thermometer, thermal expansion thermometer, magnetic thermometer, employing thermocouple, resistance thermometer, thermosensitive thermometer, semiconductor thermometer, radiation thermometer, light thermometer etc.In addition, the Temperature Detector 3 and 5 that detects the environment temperature of above-mentioned heat exchanger is not limited to detect the type of the atmosphere temperature of surroundings, and its periphery that also can be at heat exchanger detects photothermal type.
Above-mentioned compressor drive division 101a comprises temperature instruction device 4 and 6, and this temperature instruction device 4 and 6 is used to indicate the operating condition of above-mentioned refrigerating circulatory device.This temperature instruction device 4 is the 2nd surroundings temperature instruction device, the 2nd surroundings temperature instruction device output instruction signal, and this command signal is represented relative the 2nd heat exchanger (condenser) 55a, the target temperature that the user has set (instruction temperature).In addition, said temperature instruction device 6 is the 1st surroundings temperature instruction device, the 1st surroundings temperature instruction device output instruction signal, this command signal is represented relative the 1st heat exchanger (evaporimeter) 53a, the target temperature that the user has set (instruction temperature).Here, the target temperature that above-mentioned relatively condenser 55a sets is the desired value of the peripheral temperature (environment temperature) of condenser, and the target temperature that above-mentioned relatively evaporimeter 33a sets is the desired value of the peripheral temperature (environment temperature) of evaporimeter.
In addition, above-mentioned refrigerating circulatory device 101 is for carrying out the air conditioner of indoor refrigeration, usually, not relative the 2nd heat exchanger 5 of user is set the desired value of peripheral temperature, said temperature instruction device 4 is unwanted, but, such as, when being cooling operation, the heat (used heat) discarded from the 2nd heat exchanger of air conditioner is used under hot-water supply system's the situations such as occasion, and said temperature instruction device 4 is as the instruction device of output expression by the command signal of target temperature (temperature that the user the has set) THo of the hot water of hot-water supply system's supply.In addition, the command signal of said temperature instruction device 6 outputs is following data signal, this data signal represent such as, be arranged at microprocessor (microcomputer) design temperature that exported, the 1st heat exchanger (target temperature) of the inside of the remote controller in the air conditioner.But the command signal that this temperature instruction device 6 is exported is not limited to such digital command signal, and it also can be the dummy instruction signal, and this dummy instruction signal is to be installed on rotary switch in the air conditioner, that carry out temperature setting usefulness to export.
Above-mentioned compressor drive division 101a comprises: volume internal circulating load instruction department 7, these volume internal circulating load instruction department 7 bases are by said temperature detector 3,5 and the temperature information of temperature instruction device 6 output, calculate the desired refrigerating capacity of this refrigerating circulatory device (promptly, unit interval the heat exchange amount that should carry out), output expression is corresponding to the command signal (circulating mass of refrigerant information) of the volume internal circulating load of the cold-producing medium of this refrigerating capacity that has calculated (that is the volume of the Linearkompressor 1a unit interval cold-producing medium that should discharge or suck) Vco; Volume internal circulating load test section 8a, this volume cycle detection 8a of portion detect the cold-producing medium peripheral passage in fact flow through this refrigerating circulatory device cold-producing medium the volume internal circulating load (promptly, in fact, the volume of the cold-producing medium that the Linearkompressor 1a unit interval discharges or sucks) Vcd, the detection signal (circulating mass of refrigerant information) of this volume internal circulating load of output expression.
At this, above-mentioned volume internal circulating load test section 8a adopts volume-displacement, and this flowmeter is surveyed out the volume flow of the cold-producing medium that flows through in the cold-producing medium circulating path.
At this, the computational methods of the concrete volume internal circulating load in the above-mentioned volume internal circulating load test section 7 adopt following method (the 1st method) usually, promptly, according to detected temperatures (promptly, temperature by the Temperature Detector detection) temperature difference between the and instruction temperature (that is the represented target temperature of exporting from the temperature instruction device of command signal) is obtained the volume internal circulating load of the necessary cold-producing medium of refrigerating circulatory device.
But, the occasion that air conditioner is provided with less room with it is arranged at the occasion in bigger room, essential in fact refrigerating capacity is different.Such as, even the said temperature difference is identical, the necessary refrigerating capacity of the occasion that the room is bigger is bigger.
So, computational methods as the volume internal circulating load, people consider the 2nd method, in the 2nd method, calculating the computing of necessary volume internal circulating load carries out like this, variable quantity in the certain hour of the temperature difference between the detected temperatures and instruction temperature (in other words, the variable quantity in the certain hour of detected temperatures) is fed back to above-mentioned computing.Specifically, in the 2nd method,, the essential volume internal circulating load of calculating by above-mentioned the 1st method is compensated corresponding to the value (specifically, the size in the room that is freezed) of the thermic load of trying to achieve according to detected temperatures variable quantity within a certain period of time.
In addition, the computational methods of the concrete volume internal circulating load of above-mentioned volume internal circulating load instruction department 7 also can be the 3rd method, in the 3rd method, employing makes the corresponding rectangular table of group etc. of value of the value and instruction temperature of the value of volume internal circulating load and detected temperatures, not by the such feedback of above-mentioned the 2nd method, but calculate necessary volume internal circulating load by open loop.
Above-mentioned compressor drive division 101a comprises: reverser 2, and this reverser 2 forms alternating current Cd, and this alternating current Cd is supplied in the linear motor of Linearkompressor 1a as drive current; Reverser control part 20, this reverser control part 20 is controlled the action of this reverser 2 in the following manner, this mode is: from the volume internal circulating load of the cold-producing medium shown in the command signal Vco of above-mentioned volume internal circulating load instruction department 7, with difference from the volume internal circulating load Vcd of the cold-producing medium shown in the detection signal of above-mentioned volume internal circulating load test section 8a be zero.
Below Linearkompressor being carried out methods of driving control specifically describes.
The linear motor of Linearkompressor 1a is by single-phase alternating current, or the alternating current that is superimposed with direct current drives, in addition, above-mentioned Linearkompressor 1a adopts the covibration of the elastomeric element that is called spring or gas to turn round expeditiously, thus, the operating frequency of Linearkompressor, be that the vibration number of reciprocating motion of the pistons is certain basically.
So, for the method for the volume internal circulating load of the refrigerating circulatory device that adjust to adopt Linearkompressor, as below shown in, consider following several method.
At first, have following method, in the method, change, adjust the volume internal circulating load that Linearkompressor 1a discharges or sucks by the amplitude that makes the alternating current that reverser 2 exported.
In addition, drive current at reverser 2 is the occasion that is superimposed with the alternating current of direct current, can adopt following method, in the method, adjust the value of DC current, make the center of vibration of the piston in the Linearkompressor 1a near cylinder cap, thus, circulating mass of refrigerant is increased, by adjusting the value of DC current, so that circulating mass of refrigerant away from cylinder cap, thus, can be reduced in the center of the vibration of piston.In addition, also consider following method, in the method, the amplitude by making alternating current and the value one of DC current change, and adjust the volume internal circulating load.
In addition, in the occasion of the certain frequency bandwidth that comprises the resonant frequency with Linearkompressor 1a, can adopt following method, in the method, the frequency change of the output current by making reverser 2 changes the volume internal circulating load of cold-producing medium.In addition, also can adopt following method, in the method,, change the volume internal circulating load of above-mentioned cold-producing medium by making the wave form varies of the alternating current that reverser 2 exported.
Below action is described.
If the alternating current Cd that is produced by reverser 2 is added on outward on the linear motor of Linearkompressor 1a, then this linear motor drives, and the reciprocating motion of piston begins.Then, when the driving condition of Linearkompressor 1a was stablized, this Linearkompressor 1a was under certain loading condiction, and being in reciprocating motion of the pistons is the resonance driving condition of resonance state.At this moment, the frequency of the reciprocating vibration number of piston and this alternating current Cd is consistent.
Like this, drive above-mentioned Linearkompressor 1a, thus, cold-producing medium circulates in the peripheral passage of refrigerating circulatory device, at this moment, in the 2nd heat exchanger (evaporimeter) 55a, follow the liquefaction of cold-producing medium, heat is discharged towards atmosphere from this heat exchanger 55a, in addition, at the 1st heat exchanger (evaporimeter) 53a, follow the gasification of cold-producing medium, realize absorption of air heat from periphery.At this moment, cold-producing medium is in above-mentioned cold-producing medium peripheral passage, according to the sequential loop at Linearkompressor 1a, the 2nd heat exchanger 55a, flow controller 57a, the 1st heat exchanger 53a and Linearkompressor 1a.In addition, in Fig. 1, the direction that cold-producing medium circulated in the cold-producing medium peripheral passage when Cmf was illustrated in the cooling operation of refrigerating circulatory device 101 of the 1st embodiment 1.
Concrete control to the Linearkompressor of refrigerating circulatory device 101 is described below.
In this air conditioner (refrigerating circulatory device) 101, on-stream, with the environment temperature of Temperature Detector 5 detections the 1st heat exchanger 53a, detect the environment temperature of the 2nd heat exchanger 55a by Temperature Detector 3.From these each Temperature Detector 3,5 this detected environment temperature (detected temperatures) of output expression THd, the detection signal of TLd is input to respectively in the volume internal circulating load instruction department 7.In addition, from temperature instruction device 6 output instruction signals, this command signal is represented the target temperature (instruction temperature) that relative the 1st heat exchanger 53a sets, promptly, the indoor temperature TLo that the user has set represents that the command signal of this instruction temperature T lo is input in the volume internal circulating load instruction department 7.
In addition, in the 1st embodiment, because as above-mentioned, not relative the 2nd heat exchanger 55a target setting temperature, so in the control of Linearkompressor, do not adopt the output of temperature instruction device 4, but, such as, discarded used heat waits the occasion of use during the cooling operation of this refrigerating circulatory device for hot-water supply system, to the following signal of above-mentioned volume internal circulating load instruction department 7 outputs, this signal refers to represent the command signal of target temperature hot water, that the user has set (instruction temperature) Tho that supplies with from the hot-water supply system from temperature refrigerator 4.
As above-mentioned, if from Temperature Detector 3,5 detection signal and be input in the volume internal circulating load instruction department 7 from the command signal of temperature instruction device, then in volume internal circulating load instruction department 7, carry out following calculation process, in this is handled, according to temperature difference and the detected temperatures THd between the above-mentioned detected temperatures TLd and instruction temperature T lo, calculate the volume internal circulating load Vco of the desired cold-producing medium of this refrigerating circulatory device, represent that the command signal (internal circulating load information) of calculated volume internal circulating load Vco is supplied in reverser control part 20.
Generally, in the occasion of the cooling operation of air conditioner, if detected temperatures (actual room temperature) TLd is higher more than instruction temperature (target temperature) Tlo, then the desired circulating mass of refrigerant of freeze cycle is many more.In addition, in the cooling operation of air conditioner, if the environment temperature step-down of off-premises station (condenser) then the load of freeze cycle diminish, necessary circulating mass of refrigerant tails off, otherwise, if the environment temperature of off-premises station increases, then the load of freeze cycle becomes big, and it is many that necessary circulating mass of refrigerant becomes.In addition, as above-mentioned, in the occasion of utilizing for the hot-water supply system from the discarded used heat of refrigerating circulatory device, if detected temperatures THd is lower more than instruction temperature T Ho, then the desired kind of refrigeration cycle amount of freeze cycle is many more.
In addition, in the running of this air conditioner (refrigerating circulatory device) 101, detect volume (volume internal circulating load) Vcd of the cold-producing medium in fact in the cold-producing medium peripheral passage, circulate by volume internal circulating load test section 8a, represent that the detection signal (internal circulating load information) of this volume internal circulating load Vcd is supplied in above-mentioned reverser control part 20.
In addition, in reverser control part 20, according to the volume internal circulating load Vco of the cold-producing medium that calculates by volume internal circulating load instruction department 7, and the volume internal circulating load Vcd of the cold-producing medium that detects by above-mentioned volume internal circulating load 8a, control signal Sc is supplied in reverser 2.So, in reverser 2,, the action of the generation alternating current of above-mentioned reverser 2 is controlled, so that the difference between the volume internal circulating load Vcd of the volume internal circulating load Vco of cold-producing medium and cold-producing medium reduces according to control signal Sc.
Such as, the volume internal circulating load Vco of necessary cold-producing medium is big more with difference between the actual volume internal circulating load Vcd, and is big more by the amplitude of the alternating current Cd of above-mentioned reverser 2 generations, consequently, in Linearkompressor 1a, the haul distance of pistons reciprocating is big more.
Thus, the internal circulating load of the cold-producing medium of freeze cycle increases, and the heat exchange amount of unit interval increases, and the environment temperature TLd of evaporimeter 53a is near its design temperature (target temperature) TLo.
Like this, in this 1st embodiment, in the refrigerating circulatory device 101 that adopts Linearkompressor 1a, be provided with: volume internal circulating load instruction department 7, this volume internal circulating load instruction department 7 is according to the peripheral temperature of indoor heat exchanger (evaporimeter) 53a, the target temperature that the user has set to this evaporimeter 53a, and the environment temperature of outdoor heat exchanger (condenser) 55a is calculated the volume internal circulating load Vco corresponding to the cold-producing medium of the desired refrigerating capacity of this refrigerating circulatory device; Volume internal circulating load test section 8a, this volume internal circulating load test section 8a detects the volume internal circulating load Vcd of the cold-producing medium of the cold-producing medium peripheral passage of in fact flowing through refrigerating circulatory device, reverser 2 to the drive current (alternating current) that produces Linearkompressor is controlled, so that the difference between the volume internal circulating load Vcd of the volume internal circulating load Vco of cold-producing medium and cold-producing medium reduces, thus, can be corresponding between the temperature of indoor reality and the target temperature poor, with higher efficient the freeze cycle of refrigerating circulatory device is controlled.
In addition, in the 1st embodiment, because not only according to indoor temperature (environment temperature of the 1st heat exchanger 53a), and calculate the volume internal circulating load Vco of the desired cold-producing medium of this refrigerating circulatory device according to outdoor temperature (environment temperature of the 2nd heat exchanger 55a), so can make the calculated value of the volume internal circulating load of the desired cold-producing medium of refrigerating circulatory device become the value that is more suitable for operating condition.
In addition, in above-mentioned the 1st embodiment, to detect the 1st and the occasion of the environment temperature of the 2 two heat exchanger be described, but, refrigerating circulatory device 101 also can be the type of the environment temperature that only detects the 1st heat exchanger 53a, in this occasion, do not need to detect the Temperature Detector 3 of the environment temperature of the 2nd heat exchanger 55a.
Also have, in above-mentioned the 1st embodiment, volume internal circulating load test section 8a adopts the volume-displacement of the volume flow of practical measurement cold-producing medium, but, above-mentioned volume internal circulating load test section 8a is not limited to this, such as, it also can be such as following differential pressure flowmeter, this differential pressure flowmeter is inferred the flow of cold-producing medium according to the pressure differential that produces in the cold-producing medium that flows through the cold-producing medium peripheral passage, in addition, also can be other, analyzer area flowmeter, turbine flowmeter, whirlpool flowmeter, ultrasonic flowmeter, electromagnetic flowmeter etc., that measure the flow of fluid.
In addition, in above-mentioned the 1st embodiment, the occasion that to refrigerating circulatory device is the air conditioner that freezes is described, but, this refrigerating circulatory device also can be the air conditioner that heats, and in this occasion, above-mentioned the 1st heat exchanger 53a moves as condenser, the 2nd heat exchanger 55a moves as evaporimeter, and the user sets the desired value of the peripheral temperature of the 1st heat exchanger 53a that moves as condenser.
Be that the concrete control of Linearkompressor 1a of occasion of carrying out the air conditioner of warming operation is simply described to refrigerating circulatory device below.But equally in this occasion, not relative the 2nd heat exchanger 55a target setting temperature is not exported the command signal of representing target temperature (instruction temperature) THo from temperature instruction device 4.
In said temperature detector 3 and 5, detect above-mentioned each heat exchanger 53a, the environment temperature of 55a, output expression detected temperatures THd, the detection signal of TLd is from the echo signal (instruction temperature) of relative the 1st heat exchanger of temperature instruction device 6 output expression, be the command signal of the temperature T Lo in the room set of user.
In volume internal circulating load instruction department 7, carry out following calculation process, in this is handled, according to above-mentioned detected temperatures TLd, THd and instruction temperature T Lo calculate the calculation process of the volume internal circulating load Vco of the desired cold-producing medium of this refrigerating circulatory device, and the detection signal (internal circulating load information) of representing calculated volume internal circulating load Vco is supplied in reverser control part 20.
Carrying out in the air conditioner of warming operation in this wise, if detected temperatures TLd is lower more than instruction temperature T Lo, then the desired circulating mass of refrigerant of freeze cycle is many more.In addition, in this air conditioner, if the environment temperature of off-premises station uprises, then the load of freeze cycle diminishes, and necessary circulating mass of refrigerant reduces, otherwise, if the environment temperature step-down of off-premises station, then the load of freeze cycle becomes big, and necessary circulating mass of refrigerant increases.
In addition, in this air conditioner (refrigerating circulatory device), detect volume (volume internal circulating load) Vcd of the cold-producing medium that in fact in the cold-producing medium peripheral passage, circulates with volume internal circulating load test section 8a, the command signal (internal circulating load information) of representing this volume internal circulating load Vcd is supplied in above-mentioned reverser control part 20, control signal Sc by above-mentioned reverser control part 20 controls the action of above-mentioned reverser 2, so that the difference between the volume internal circulating load Vcd of the volume internal circulating load Vco of cold-producing medium and cold-producing medium reduces.
In such air conditioner that carries out warming operation, identical with the air conditioner that carries out cooling operation of the foregoing description, because the reverser 2 to the drive current (alternating current) that produces above-mentioned Linearkompressor 1a is controlled, make the difference between the volume internal circulating load Vcd of the volume internal circulating load Vco of desired cold-producing medium and actual cold-producing medium reduce, so can be corresponding between the temperature of indoor reality and the target temperature poor, with the refrigerating capacity of higher control from view of profit refrigerating circulatory device.
In addition, in the present embodiment, provide the occasion that refrigerating circulatory device is an air conditioner, above-mentioned refrigerating circulatory device is not limited thereto, and it is refrigerating box, hot water supply apparatus, utmost point low-temperature freezing facilities etc. also.
(the 2nd embodiment)
Fig. 2 is the block diagram that is used to illustrate the refrigerating plant of the 2nd embodiment of the present invention.
The refrigerating circulatory device 102 of the 2nd embodiment comprises the following driven compressor 102a of portion, the 101a of driven compressor portion with the refrigerating circulatory device 101 that replaces the 1st embodiment, the difference of this 102a of driven compressor portion and the 101a of this driven compressor portion is to detect the volume internal circulating load of actual cold-producing medium, and other composition is identical with the occasion of the 1st embodiment.
Promptly, above-mentioned compressor drive division 102a is identical with the 101a of driven compressor portion of the 1st embodiment, comprises the 2nd surroundings Temperature Detector the 3, the 1st surroundings detector the 5, the 2nd surroundings temperature instruction device the 4, the 1st surroundings temperature instruction device 6, volume internal circulating load instruction device 7, reverser 2 and reverser control part 20.
In addition, the 102a of driven compressor portion of this 2nd embodiment comprises: stroke detection portion 9, and the trip test section 9 detects the haul distance of the piston that moves back and forth in the inside of Linearkompressor 1a; Upper dead center position test section 10, this upper dead center position test section 10 detects at the upper dead center position of the piston of the reciprocates inside of Linearkompressor 1a, is the piston position Dfd during close cylinder cap of piston, the detection signal (upper dead center position information) of this upper dead center position of output expression; Volume internal circulating load test section 8b, this volume internal circulating load test section 8b be according to above-mentioned haul distance Dps and upper dead center position Dfd, calculates the volume internal circulating load Vcd of reality of the cold-producing medium of the cold-producing medium peripheral passage of flowing through refrigerating circulatory device 102.
Here, above-mentioned stroke test section 9 and upper dead center position test section 10 adopt the position sensor of contact-type.But, above-mentioned each test section is not limited to the position sensor of contact-type, also can be the position sensor of non-contact type, such as, the gap of eddy current type (gap) sensor, adopt the differential transformer of 2 coils, in addition, also can be according to being input to the electric current in the Linearkompressor and the value of voltage and infer the haul distance of above-mentioned piston and the type of upper dead center position.
Below action is described.
In the refrigerating circulatory device 102 of the 2nd embodiment, different with the 1st embodiment of the action of the volume internal circulating load of only obtaining actual cold-producing medium, below, mainly the action to the volume internal circulating load of obtaining actual cold-producing medium is described.
When in the inside of Linearkompressor 1a, when cold-producing medium was compressed, in the supposition occasion of situations such as leakage not, the state variation of this cold-producing medium was heat insulation variation.So, if the pressure of cold-producing medium is represented that by P its volume is represented that by V specific heat ratio is represented that by γ then following formula (1) is set up.
P * V γ=certain ... (1)
In addition, above-mentioned specific heat ratio γ refers to the specific heat at constant pressure Cp of above-mentioned cold-producing medium and the ratio of specific heat at constant volume Cv, and it is difference owing to the kind of cold-producing medium.
Below following method is described, this method is obtained the volume of a cold-producing medium of back and forth discharging from Linearkompressor 1a of following piston according to the haul distance of piston and upper dead center position.
Fig. 3 is the figure of the position of the piston 72 of the inside of expression cylinder 71, when Fig. 3 (a) is illustrated in piston 72 and is positioned at upper dead center position, the appearance of piston during near cylinder cap, when Fig. 3 (b) is illustrated in piston 72 and is positioned at lower dead point position, the appearance of piston during away from cylinder cap.
As shown in Fig. 3 (a), when piston 72 is positioned at upper dead center position, the pressure P x of the cold-producing medium of the inside of discharge chambe 76 is pressure P 1 (Pa).In addition, under the state that cold-producing medium is circulated in freeze cycle (peripheral passage of cold-producing medium), when piston was positioned at upper dead center position, the internal pressure Px of discharge chambe 76 rose to pressure (discharge pressure) Pd (Pa) of cold-producing medium when Linearkompressor is discharged.The pressure P 1 (Pa) of the cold-producing medium when thus, piston is positioned at upper dead center position equals above-mentioned discharge pressure Pd (Pa).
In addition, the volume Vx of discharge chambe 76 is minimum, the volume V1 (m of the discharge chambe of this moment when piston 72 is positioned at upper dead center position 3) obtain as following product, this product is the cylinder cap inner face of piston 72 when upper dead center position and the sectional area S (m of spacing x1 (m) between the piston compressing surface and piston 2) product.
As shown in Fig. 3 (b), when piston 72 is positioned at lower dead point position, the pressure P x of the cold-producing medium of discharge chambe inside is pressure P 2 (Pa).In addition, at the state of cold-producing medium in the freeze cycle inner loop, when piston was positioned at lower dead point position, it was pressure (suction pressure) Ps (Pa) of Linearkompressor when absorbing that discharge chambe pressure inside Px reduces to cold-producing medium.Refrigerant pressure P2 (Pa) when thus, piston is positioned at lower dead point position equals suction pressure Ps (Pa).
In addition, the volume Vx of discharge chambe becomes maximum when piston 72 is positioned at lower dead point position, the volume V2 (m of the discharge chambe of this moment 3) can obtain by following product, this product refer to piston 72 when lower dead point position the cylinder cap inner face and the spacing x3 (m) between the piston compressing surface, with the sectional area S (m of piston 2) product.In addition, here, above-mentioned spacing x3 (m) be spacing x1 (m) with length of piston travel x2's (m) and.
As shown in Fig. 3 (c), if piston begins to shift to the cylinder cap side from its lower dead point position, then Linearkompressor is in compressive state.At this moment, the volume Vx of discharge chambe begins to reduce, and discharge chambe pressure inside Px begins to rise from suction pressure P2.Then, when discharge chambe pressure inside Px rose to discharge pressure P1, the dump valve of Linearkompressor 1a was opened, and the discharge of cold-producing medium is begun.The volume Vx of the discharge chambe of this moment is volume V3.
In the compression travel of Linearkompressor, piston from lower dead point position (Fig. 3 (b) move to the position that dump valve opens (Fig. 3 (c) during, the cold-producing medium of discharge chambe inside changes in heat insulation mode, following formula (2) is set up.
P2×V2γ＝P1×V3γ …(2)
So the volume of the cold-producing medium of being discharged is obtained by following formula (3).
V3-V1＝(P2/P1)1/γ×V2-V1 …(3)
On the other hand, in the suction stroke at Linearkompressor, the volume of the discharge chambe when discharge chambe pressure inside Px arrives suction pressure Ps is by V4 (m 3) when representing, the volume of the cold-producing medium that is sucked is obtained by following formula (4).
V2-V4＝V2-(P1/P2)1/γ×V1 …(4)
In addition, in the 2nd embodiment, the representational value when pressure ratio (P1/P2) in above-mentioned formula (3) and the formula (4), discharge pressure and suction pressure adopts in freeze cycle motion.
In addition, in Linearkompressor 1a, owing to carry out the reciprocating motion of piston, so the reciprocating number of times of the piston that carries out of unit interval is consistent with the frequency of the output current of reverser according to the frequency identical with the drive current of being imported.
So, in above-mentioned volume internal circulating load test section 8b, the volume of the cold-producing medium of being discharged at the unit interval Linearkompressor is obtained in the volume that by the piston obtained by above-mentioned (3) formula 1 time moves back and forth the cold-producing medium of discharging and the multiplying processing of the frequency of reverser.In addition, in above-mentioned volume internal circulating load test section 8b, the volume of the cold-producing medium that is sucked at the unit interval Linearkompressor is obtained in the volume that by the piston obtained by above-mentioned (4) 1 time moves back and forth the cold-producing medium that sucks and the multiplying processing of the frequency of reverser.
In addition, from above-mentioned volume internal circulating load test section 8b output detection signal (internal circulating load information), this detection signal will be by representing as the internal circulating load of the cold-producing medium of reality according to the volume Vcd of unit interval by the cold-producing medium of Linearkompressor discharge or suction, this detection signal is supplied with above-mentioned reverser control part 20, at this moment, export the control signal Sc of reversers 2 from this reverser control part 20.So, in reverser 2,, the generation action of alternating current is controlled the difference minimizing of the volume internal circulating load Vcd of the volume internal circulating load Vco of the cold-producing medium of feasible necessity and reality according to above-mentioned control signal Sc.
Like this, in the 2nd embodiment, owing to comprise: stroke detection portion 9, the trip test section 9 detects the haul distance at the piston of the reciprocates inside of Linearkompressor 1a; Upper dead center position test section 10, this upper dead center position test section 10 detects the upper dead center position at the piston of the reciprocates inside of Linearkompressor 1a, haul distance according to above-mentioned piston, upper dead center position and as the frequency of the output AC electric current of the reverser 2 of the drive current of Linearkompressor 1a, the volume internal circulating load of the cold-producing medium of the reality that calculating circulates in freeze cycle, so have following effect, promptly, identical with above-mentioned the 1st embodiment, the temperature of the reality in the room that can corresponding be freezed and target temperature poor, adopt the refrigerating capacity of the refrigerating circulatory device of Linearkompressor with higher control from view of profit, and do not need to measure the fluid sensor of the volume internal circulating load of actual cold-producing medium.
In addition, in above-mentioned the 2nd embodiment, in a calculating of the volume of the cold-producing medium of discharging or sucking, the pressure ratio of discharge pressure and suction pressure (P1/P2) adopts the representational value when moving in freeze cycle, but this pressure ratio also can be the value of obtaining by the discharge pressure of practical measurement cold-producing medium and suction pressure.In this occasion, equally because in the refrigerating circulatory device that the operating condition pressure state changes, the discharge pressure of cold-producing medium and the pressure ratio variation of suction pressure are such, can be according to the volume internal circulating load of cold-producing medium, with the condensation ability of good efficiency control refrigerating circulatory device.
Here, ask the method for discharge pressure value to include following method, promptly, according to the temperature as the heat exchanger of condenser of discharge side in the 1st heat exchanger that constitutes freeze cycle and the 2nd heat exchanger, that be arranged at compressor, the pressure with the value of above-mentioned discharge pressure during and obtaining as cold-producing medium saturated.In addition, in the method for the value of obtaining suction pressure, comprise following method, promptly, according to the temperature as the heat exchanger of cold evaporimeter of discharge side in the 1st heat exchanger that constitutes freeze cycle and the 2nd heat exchanger, that be arranged at compressor, the pressure with the value of above-mentioned suction pressure during and obtaining as cold-producing medium saturated.
That is, if under the condition of certain certain pressure, refrigerating fluid is heated, when the temperature of this liquid rises and when arriving certain temperature, refrigerating fluid comes to life.At this state, even also refrigerating fluid is heated, this temperature still remains on certain value, evaporates fully until refrigerating fluid.In addition, if under the condition of certain certain pressure refrigerant gas is cooled off, when arriving certain temperature when this gas temperature reduction, then refrigerant gas begins condensation.At this state, even also refrigerant gas is cooled off, this temperature still remains on certain value, until the whole condensations of refrigerant gas.Like this, even under the situation that cold-producing medium is heated or cool off, the temperature that temperature still remains on the cold-producing medium of certain state is a saturation temperature, and the pressure of the cold-producing medium of this moment is saturation pressure.Usually, in the inside of evaporimeter or condenser, make the pressure of cold-producing medium keep certain, cold-producing medium is in the saturation state under the state of its liquid and vapor mixing.Relation between temperature when in addition, being in saturation state (saturation temperature) and the pressure (saturation pressure) is determined by cold-producing medium.Therefore, if can measure the saturation temperature of cold-producing medium, then can obtain saturation pressure.
(the 3rd embodiment)
Fig. 4 is the block diagram that is used to illustrate the refrigerating circulatory device of the 3rd embodiment of the present invention, and its expression constitutes the Linearkompressor drive division of this refrigerating circulatory device.
The refrigerating circulatory device 103 of the 3rd embodiment comprises following Linearkompressor drive division 103a, this Linearkompressor drive division 103a replaces according to the volume internal circulating load (also only being referred to as the volume internal circulating load below) of the unit interval of cold-producing medium Linearkompressor 1a being driven the Linearkompressor drive division 101a of control, this Linearkompressor drive division 103a drives control Linearkompressor 1a according to the weight internal circulating load (also only being referred to as the weight internal circulating load below) of the unit interval of cold-producing medium, and other composition is identical with the occasion of the refrigerating circulatory device 101 of the 1st embodiment.
Promptly, above-mentioned refrigerating circulatory device 103 is identical with the refrigerating circulatory device 101 of the 1st embodiment, be the air conditioner that carries out indoor refrigeration, it comprises: the 2nd heat exchanger (condenser) 55a and the 1st heat exchanger (evaporimeter) 53a that form the peripheral passage (freeze cycle) of cold-producing medium; Linearkompressor 1a, this Linearkompressor are arranged at the gas side flow passage Gp that connects above-mentioned two heat exchangers; Expansion valve 57a, this expansion valve 57a are arranged at the hydraulic fluid side flow passage Lp that connects above-mentioned two heat exchangers.
Above-mentioned Linearkompressor drive division 103a is identical with the Linearkompressor drive division 101a of the refrigerating circulatory device 101 of the 1st embodiment, comprising: reverser 2, the alternating current that this reverser 2 produces as the drive current of Linearkompressor; Temperature Detector 3, this Temperature Detector 3 detects the environment temperature of the 2nd heat exchanger; Temperature instruction device 4, the environment temperature of this temperature instruction device 4 indications the 2nd heat exchanger; Temperature Detector 5, this Temperature Detector 5 detects the environment temperature of the 1st heat exchanger; Temperature instruction device 6, the environment temperature of this temperature instruction device 6 indications the 1st heat exchanger.
In addition, above-mentioned Linearkompressor drive division 103a comprises: weight internal circulating load instruction department 11, this weight internal circulating load instruction department 11 is according to the output of above-mentioned each Temperature Detector 3,5 and temperature instruction device 4, calculate the desired refrigerating capacity of freeze cycle, the output expression is corresponding to the command signal (internal circulating load information) of the weight internal circulating load Wco of the cold-producing medium of this refrigerating capacity that calculates; Weight internal circulating load test section 12c, this weight internal circulating load test section 12c detects the weight internal circulating load of the cold-producing medium that in fact flows through freeze cycle (cold-producing medium peripheral passage), the output signal (internal circulating load information) of the weight internal circulating load Wcd of the cold-producing medium that the output expression is actual; Reverser control part 21,21 pairs of reversers 2 that produce drive current (alternating current) Id of above-mentioned Linearkompressor 1a of this reverser control part are controlled, and make that the internal circulating load Wcd of above-mentioned reality and the difference between the above-mentioned desired internal circulating load Wco are zero.Here, above-mentioned weight internal circulating load test section 12c adopts following Coriolis (Coriolis) mass flowmenter, this mass flowmenter quality measurement flow (that is, the unit interval is flow through the quality of the cold-producing medium of freeze cycle).
In addition, identical with the 1st embodiment in the 3rd embodiment, not relative the 2nd heat exchanger target setting temperature, thus, the output of temperature instruction device 4 is not adopted in the control of Linearkompressor.But, such as, the used heat of being discarded during the cooling operation of this refrigerating circulatory device waits the occasion of utilizing for hot-water supply system, the command signal of target temperature hot water, that the user has set (instruction temperature) Hlo that supplies with by the hot-water supply system to above-mentioned weight internal circulating load instruction department 11 output expressions from temperature instruction device 4.
Below action is described.
In the refrigerating circulatory device 103 of the 3rd embodiment, the desired refrigerating capacity of this refrigerating circulatory device is as the 1st embodiment, according to the volume internal circulating load of cold-producing medium and controlled, and controlled according to the weight internal circulating load of cold-producing medium.Therefore, mainly following actions is described below, this action refers to drive the Linearkompressor of controlling in the refrigerating circulatory device according to the weight internal circulating load of cold-producing medium.
Drive Linearkompressor 1a by Linearkompressor drive division 103a, cold-producing medium circulates in inside, cold-producing medium peripheral passage, carry out heat exchange with each heat exchanger, under this state, in each Temperature Detector 3,5, detect the environment temperature of the 2nd heat exchanger (condenser) 55a and the 1st heat exchanger (evaporimeter) 53a, the detection signal (temperature information) of representing detected environment temperature is supplied in weight internal circulating load instruction department 11.In addition, from temperature instruction device 6 output following command signals (temperature information), it is supplied with above-mentioned weight recursion instruction portion 11, and this command signal is represented the target temperature (that is the desired value of evaporimeter environment temperature) that relative the 1st heat exchanger (evaporimeter) 53a user has set.
Then, in above-mentioned weight internal circulating load instruction department 11, according to from the temperature information (detection signal) of Temperature Detector 3,5 and from the temperature information (command signal) of temperature instruction device 6, carry out the computing of this refrigerating circulatory device 103 desired cold-producing medium weight internal circulating loads, the command signal (internal circulating load information) of representing the weight internal circulating load Wco of this cold-producing medium that has calculated is exported to reverser control part 21.Here, in above-mentioned weight internal circulating load instruction department 11, the calculation process of calculated weight internal circulating load forms the variable quantity of certain unit interval of the temperature difference of detected temperatures TLd and instruction temperature T lo as feedback.That is, calculate necessary weight internal circulating load, this calculated weight internal circulating load is carried out revisal according to the variable quantity of certain unit interval of detected temperatures TLd and instruction temperature T lo according to the difference of detected temperatures TLd and instruction temperature T lo and detected temperatures THd one meaning ground.With expression this revisal the command signal of weight internal circulating load of cold-producing medium supply with reverser control part 21.
In addition, in above-mentioned weight internal circulating load test section 12, analyzer by Coriolis (Coriolis) mass flowmenter etc., mensuration flows through the weight internal circulating load of reality of the cold-producing medium of above-mentioned peripheral passage, and the detection signal (internal circulating load information) of the weight internal circulating load of the reality of the cold-producing medium that expression has been measured is exported to above-mentioned reverser control part 21.
So, supply with control signal Sc from above-mentioned reverser control part 21 to reverser 21, in reverser 2, according to this control signal Sc the generation action of alternating current is controlled, make the weight internal circulating load Wco of cold-producing medium and the poor of weight internal circulating load Wcd of cold-producing medium reduce.
Like this, in the 3rd embodiment, owing to be provided with in the refrigerating circulatory device 103 that adopts Linearkompressor 1a: the environment temperature of indoor target temperature that weight internal circulating load instruction department 11, this weight internal circulating load instruction department 11 have been set according to environment temperature, the user of indoor heat exchanger (evaporimeter) 53a and outdoor heat exchanger (condenser) 55a is calculated the weight internal circulating load Wco corresponding to the cold-producing medium of the desired refrigerating capacity of this refrigerating circulatory device; The weight cycle detection 12c of portion, this weight cycle detection 12c of portion detects the weight internal circulating load Wcd of the cold-producing medium of the freeze cycle path that in fact flows through this refrigerating circulatory device; Reverser 2, this reverser 2 produces the alternating current that drives Linearkompressor 1a, above-mentioned reverser 2 is controlled, make the weight internal circulating load Wco of above-mentioned cold-producing medium and the poor of weight internal circulating load Wcd of cold-producing medium reduce, so can with good efficiency the refrigerating capacity of refrigerating circulatory device be controlled corresponding to the temperature of the reality in the room that is freezed and the temperature difference between the target temperature.In addition, in the 3rd embodiment, owing to the basis and the weight internal circulating load of the more closely-related cold-producing medium of load of this device are controlled the refrigerating capacity of refrigerating circulatory device, so can better response stably refrigerating capacity be controlled.
In addition, in the 3rd embodiment, because not only according to indoor temperature (environment temperature of evaporimeter), but also calculate the weight internal circulating load Wco of the desired cold-producing medium of this refrigerating circulatory device according to outdoor temperature (environment temperature of condenser), be the value that is more suitable for operating condition so can make the calculated value of the weight internal circulating load of the desired cold-producing medium of refrigerating circulatory device.
In addition, in the 3rd embodiment, provide above-mentioned weight recursion instruction portion 11 for the variation of the temperature difference of detected temperatures and instruction temperature is calculated the type of necessary weight internal circulating load as feedback, but above-mentioned weight internal circulating load instruction department 11 also can form like this, promptly, employing makes the corresponding rectangular table of group etc. of value of the value and instruction temperature of the value of weight internal circulating load and detected temperatures, not by feedback loop as described above, but, calculate necessary weight internal circulating load by open loop.
Also have, in above-mentioned the 3rd embodiment, providing weight internal circulating load test section 12c is the occasion of Coriolis (Coriolis) mass flowmenter of quality measurement flow, but, weight internal circulating load test section 12c also can adopt the analyzer of thermal mass flow meter etc., in this occasion, obtain the effect identical equally with the 3rd embodiment.
Have again, in the present embodiment, at refrigerating circulatory device is that the occasion of carrying out the air conditioner of indoor refrigeration is described, but, the refrigerating circulatory device of the 3rd embodiment also can be described as the 1st embodiment, both can be the air conditioner that carries out indoor heating, also can be refrigerating box, hot water supply apparatus, utmost point low-temperature freezing facilities etc.
(the 4th embodiment)
Fig. 5 is the block diagram that is used to illustrate the refrigerating circulatory device of the 4th embodiment of the present invention.
The refrigerating circulatory device 104 of the 4th embodiment comprises the 104a of driven compressor portion, to replace the 103a of driven compressor portion of the 3rd embodiment, the difference of this driven compressor portion 104 and the 103a of driven compressor portion is to detect the method for the weight internal circulating load of cold-producing medium, and other composition is identical with the occasion of the 3rd embodiment.
Promptly, above-mentioned compressor drive division 104a is identical with the 103a of driven compressor portion of the 3rd embodiment, comprises the 2nd surroundings Temperature Detector the 3, the 1st surroundings Temperature Detector the 5, the 2nd surroundings temperature instruction device the 4, the 1st surroundings temperature instruction device 6, weight internal circulating load instruction department 11, reverser 2 and reverser control part 21.
In addition, the 104a of driven compressor portion of the 4th embodiment comprises: stroke detection portion 9, the trip test section 9 detects the haul distance at the piston of the reciprocates inside of Linearkompressor 1a, the detection signal (travel information) of the detected haul distance Dps of output; Upper dead center position test section 10, this upper dead center position test section 10 detects at the upper dead center position of the piston of the reciprocates inside of Linearkompressor 1a, is the piston position Dfd during close cylinder cap of piston, the detection signal (upper dead center position information) of this upper dead center position of output expression; Discharging refrigerant Density Detection portion 13, this discharging refrigerant Density Detection portion 13 is detected from the density D md1 of the cold-producing medium of Linearkompressor 1a discharge; Weight internal circulating load test section 12d, this weight internal circulating load test section 12d calculate the weight internal circulating load Wcd of reality of the cold-producing medium of the cold-producing medium peripheral passage of flowing through refrigerating circulatory device according to above-mentioned haul distance Dps, upper dead center position Dfd and refrigerant density Dmd1.Here, discharging refrigerant Density Detection portion 13 adopts the density sensor that uses optical fiber.In addition, above-mentioned stroke test section 9 is identical with the 2nd embodiment with upper dead center position test section 10, adopts the position sensor of contact-type.But, above-mentioned each test section is not limited to the position sensor of contact-type, also can adopt the position sensor of non-contact type, such as, the gap of eddy current type (gap) sensor or adopt the differential transformer of 2 coils, also can be following type in addition, it infers the haul distance and the upper dead center position of above-mentioned piston according to being input to the electric current in the Linearkompressor and the value of voltage.
Below action is described.
In the refrigerating circulatory device 104 of the 4th embodiment, the action of weight internal circulating load of reality of only calculating the cold-producing medium flow through the cold-producing medium peripheral passage is different with the 3rd embodiment, below mainly the calculating of the weight internal circulating load of above-mentioned cold-producing medium is moved and is described.
In stroke test section 9, detect the length of piston travel Dps of the Linearkompressor 1a in the running, the detection signal (travel information) of expression haul distance is exported to weight internal circulating load test section 12d.In addition, in above-mentioned upper dead center position test section 10, detect the piston upper dead center position Dfd of the Linearkompressor in the running, the detection signal (upper dead center position information) of expression upper dead center position is exported to weight internal circulating load test section 12d.In addition, in discharging refrigerant Density Detection portion 13, detect, the detection signal (density information) of expression refrigerant density is exported to the above-mentioned weight cycle detection 12d of portion from the density D md1 of the cold-producing medium of Linearkompressor 1 discharge.
So, in above-mentioned weight internal circulating load test section 12d, identical with the volume internal circulating load test section 8b of the refrigerating circulatory device 102 of the 2nd embodiment, according to length of piston travel Dps and upper dead center position Dfd, obtain the volume of the cold-producing medium that the each reciprocating motion of the pistons of Linearkompressor 1a discharged.In this weight internal circulating load test section 12d, also carry out above-mentioned volume that obtained, the discharging refrigerant of reciprocating motion of the pistons each time and handle, the cold-producing medium weight that the reciprocating motion each time of calculating piston is discharged with multiplying by the 13 detected discharging refrigerant density D ms1 of discharging refrigerant Density Detection portion.In addition, in this weight internal circulating load test section 12d, carry out the processing that the frequency with the weight that once moves back and forth the cold-producing medium discharged of piston and reverser multiplies each other, obtain the weight W cd of the cold-producing medium that the time per unit Linearkompressor discharged, detection signal (internal circulating load information) that will this discharging refrigerant weight of expression is supplied with reverser control part 21.So, Sc is supplied in reverser 2 from reverser control part 21 with its control signal, in reverser 2, according to above-mentioned control signal Sc the generation of above-mentioned alternating current action is controlled, made the difference of weight internal circulating load Wco and the weight internal circulating load Wcd of actual cold-producing medium of desired cold-producing medium reduce.
Like this, in the 4th embodiment, because it comprises: stroke detection portion 9, the trip test section 9 detects the haul distance at the piston of the reciprocates inside of Linearkompressor 1a; Upper dead center position test section 10, this upper dead center position test section 10 detects the upper dead center position at the piston of the reciprocates inside of Linearkompressor 1a; Discharging refrigerant Density Detection portion 13, this discharging refrigerant Density Detection portion 13 is detected from the density of the cold-producing medium of Linearkompressor 1 discharge, according to above-mentioned length of piston travel, upper dead center position, the density of the cold-producing medium of discharging from Linearkompressor 1a and as the frequency of the output AC electric current of the reverser 2 of the drive current of Linearkompressor, the weight internal circulating load of the cold-producing medium of the reality that calculating circulates in freeze cycle, so it is identical with the 3rd embodiment, has following effect, promptly, can be corresponding to the temperature of the reality in the room that is freezed and the temperature difference between the target temperature with higher efficient to as adopting Linearkompressor, carrying out the refrigerating capacity of refrigerating circulatory device of the air conditioner of indoor refrigeration controls, has following effect in addition, that is, can not need to measure the fluid sensor of the weight internal circulating load of actual cold-producing medium.
In addition, in above-mentioned the 4th embodiment, provided the occasion of discharging refrigerant Density Detection portion 13 for the density sensor of employing optical fiber, but above-mentioned discharging refrigerant Density Detection portion 13 also can be the type of obtaining the density of discharging refrigerant according to the pressure of the temperature of discharging refrigerant and discharging refrigerant.In this occasion, can not adopt the sensor of the density of measuring discharging refrigerant just can control the refrigerating capacity of refrigerating circulatory device expeditiously.
In addition, concrete grammar as according to the density of the calculation of pressure discharging refrigerant of the temperature of discharging refrigerant and discharging refrigerant includes: carry out Calculation Method, carry out Calculation Method according to the corresponding table of group of the value of the value of the temperature of density that makes cold-producing medium and cold-producing medium and pressure according to the equation of state of cold-producing medium.Here; the temperature of discharging refrigerant can generally be obtained according to following output; this output refers to the output as the temperature sensor at the outlet place sensor of the protection usefulness of Linearkompressor 1a, that be installed on Linearkompressor 1a; in addition, the pressure of discharging refrigerant can calculate according to the output of the pressure sensor of the discharge side that is installed on Linearkompressor 1a.In addition, the pressure of discharging refrigerant is as described at the 2nd embodiment, also can be according to following temperature pressure during as cold-producing medium saturated obtain, this temperature refers to constitute the temperature as the heat exchanger of condenser of discharge side in the 1st heat exchanger of freeze cycle and the 2nd heat exchanger, that be arranged at Linearkompressor 1a.
(the 5th embodiment)
Fig. 6 is the block diagram that is used to illustrate the refrigerating circulatory device of the 5th embodiment of the present invention.
The refrigerating circulatory device 105 of present embodiment 5 comprises Linearkompressor 105a, make to replace the 4th embodiment, according to the Linearkompressor 104a of the weight internal circulating load of the cold-producing medium of the density calculation reality of the cold-producing medium of discharging from Linearkompressor 1a, this Linearkompressor 105a is according to the weight internal circulating load of the cold-producing medium of the density calculation reality that is drawn into the cold-producing medium among the Linearkompressor 1a, and other composition is identical with the occasion of the 4th embodiment.
Promptly, 105a is identical with the 4th embodiment for this Linearkompressor drive division, comprises the 2nd surroundings Temperature Detector the 3, the 1st surroundings Temperature Detector the 5, the 2nd surroundings temperature instruction device the 4, the 1st surroundings temperature instruction device 6, stroke detection portion 9, upper dead center position detector 10, weight internal circulating load instruction department 11, reverser 2 and reverser control part 21.
In addition, the 105a of driven compressor portion of this 5th embodiment comprises: suck refrigerant density test section 14, this suction refrigerant density test section 14 detects the density D md2 that is drawn into the cold-producing medium among the Linearkompressor 1a; The weight cycle detection 12e of portion, this weight cycle detection 12e of portion is according to the weight internal circulating load Wcd of the cold-producing medium of the reality of length of piston travel Dps, upper dead center position Dfp and suction refrigerant density Dmd2 calculating Linearkompressor 1a.Here, above-mentioned suction refrigerant density test section 14 adopts the density sensor of use optical fiber etc.
Below action is described.
In the refrigerating circulatory device 105 of the 5th embodiment, the action of weight internal circulating load of only calculating actual cold-producing medium is different with the 4th embodiment, below mainly the calculating of the weight internal circulating load of cold-producing medium is moved and is described.
Driving Linearkompressor 1a, cold-producing medium is at the state of the inner loop of peripheral passage, in stroke test section 9, detect the length of piston travel Dps among the Linearkompressor 1a in the running, the detection signal (travel information) of expression haul distance is exported to weight internal circulating load test section 12e.In addition, in upper dead center position test section 10, detect the piston upper dead center position Dfd of the Linearkompressor in the running, the detection signal (upper dead center position information) of expression upper dead center position is exported to weight internal circulating load test section 12e.In addition, in sucking refrigerant density test section 14, detect the density D md2 that is drawn into the cold-producing medium among the Linearkompressor 1a, the detection signal (density information) of expression refrigerant density is exported to the above-mentioned weight cycle detection 12e of portion.
So, in above-mentioned weight internal circulating load test section 12e, identical with the volume internal circulating load test section 8b in the refrigerating circulatory device 102 of the 2nd embodiment, according to length of piston travel and upper dead center position, obtain the volume of the reciprocal cold-producing medium that is sucked for 1 time of Linearkompressor 1a piston.In this weight internal circulating load test section 12e, also carry out following processing, this processing refers to the volume of the every reciprocal 1 time suction cold-producing medium of above-mentioned that obtain, piston, handle with the multiplying of density by sucking the suction cold-producing medium that refrigerant density test section 14 detects, calculate the weight of the reciprocal cold-producing medium that is sucked for 1 time of piston.In addition, in this weight internal circulating load test section 12e, carry out the processing that the weight of the cold-producing medium that the reciprocating motion with the frequency of the output current of reverser and piston sucked for 1 time multiplies each other, obtain the weight W cd2 of the cold-producing medium that the time per unit Linearkompressor sucked, the detection signal (internal circulating load information) that will expression sucks cold-producing medium weight is supplied with above-mentioned reverser control part 21.
So, supply with its control signal Sc from reverser control part 21 to reverser 2, in reverser 2, according to this control signal Sc the generation action of above-mentioned alternating current is controlled, make the weight internal circulating load Wco of cold-producing medium and the poor of weight internal circulating load Wcd of cold-producing medium reduce.
Like this, in this 5th embodiment, because it comprises: stroke detection portion 9, the trip test section 9 detects the haul distance Dps at the piston of the reciprocates inside of Linearkompressor 1a; Upper dead center position test section 10, this upper dead center position test section 10 detects the upper dead center position Dfd at the piston of the reciprocates inside of above-mentioned Linearkompressor 1a; Suck refrigerant density test section 14, this suction refrigerant density test section 14 detects the density D md2 that is drawn into the cold-producing medium among the Linearkompressor 1a, haul distance according to above-mentioned piston, upper dead center position, be drawn into the density of the cold-producing medium in the Linearkompressor and as the frequency of the output AC electric current of the reverser 2 of the drive current of Linearkompressor 1a, the weight internal circulating load of the cold-producing medium of the reality that calculating circulates in freeze cycle, so it is identical with above-mentioned the 3rd embodiment, has following effect, promptly, refrigerating capacity as the refrigerating circulatory device of the indoor air conditioner that freezes is controlled with higher efficient corresponding to the temperature difference of the temperature of the reality in the room that is freezed and target temperature, also has following effect in addition, that is, can need not to measure the fluid sensor of the weight internal circulating load of actual cold-producing medium.Such as, hypertonia at discharging refrigerant, the density of discharging refrigerant can not detected occasion, do not adopt the sensor of gravimetry internal circulating load, and only adopt to suck the sensor of the density of cold-producing medium, just can control the refrigerating capacity of refrigerating circulatory device according to the weight internal circulating load of cold-producing medium expeditiously.
In addition, in above-mentioned the 5th embodiment, provide suck refrigerant density test section 14 for adopt optical fiber the occasion of density sensor, but above-mentioned suction refrigerant density test section 14 also can be the type that sucks the density of cold-producing medium according to temperature that sucks cold-producing medium and the calculation of pressure that sucks cold-producing medium.
Equally in this occasion, hypertonia at discharging refrigerant, the state that the pressure of discharging refrigerant can not detect does not adopt the sensor of measuring the density that sucks cold-producing medium just can control the refrigerating capacity of refrigerating circulatory device according to the weight internal circulating load of cold-producing medium expeditiously.
In addition, suck the method for the density of cold-producing medium as calculation of pressure according to temperature that sucks cold-producing medium and suction cold-producing medium, include the method for the equation of state that adopts cold-producing medium, adopt the method for the corresponding table of group of the value of the value of the temperature that makes this density and cold-producing medium and pressure.
Here, the temperature that sucks cold-producing medium can be obtained according to the output of the temperature sensor on the suction inlet that is installed on Linearkompressor 1a.In addition, the pressure that sucks cold-producing medium can be obtained according to the output of the pressure sensor of the suction side that is arranged at Linearkompressor 1a.In addition, the pressure that sucks cold-producing medium can resemble equally as described in the 2nd embodiment, according to following temperature, pressure as cold-producing medium when saturated and obtaining, this temperature refer to constitute the temperature as the heat exchanger of evaporimeter of suction side in the 1st heat exchanger of freeze cycle and the 2nd heat exchanger, that be arranged at Linearkompressor 1a.In addition, the detection method that sucks the temperature of cold-producing medium is not limited to the method that the temperature sensor by the suction inlet that is installed on Linearkompressor 1a detects, also can such as, infer the degree of superheat relevant (promptly with freeze cycle, be drawn into the temperature of the cold-producing medium in the Linearkompressor and the temperature difference between the saturation temperature), according to this degree of superheat with as the temperature of the heat exchanger of evaporimeter and, infer the temperature that sucks cold-producing medium.In this occasion, even hypertonia at discharging refrigerant, under the situation that the pressure of discharging refrigerant can not detect, still can not adopt the sensor of the density that measure to suck cold-producing medium and the sensor of measuring the temperature that sucks cold-producing medium, and according to effectively the ability of refrigerating circulatory device being controlled with the weight circulation that the load of refrigerating circulatory device more closely contacts relevant cold-producing medium.
(the 6th embodiment)
Fig. 7 is the block diagram of the air conditioner of explanation the 6th embodiment of the present invention.
The air conditioner 106 of the 6th embodiment is the air conditioner that comprises that indoor set 114 and indoor set 115 freeze, and the difference of the air conditioner 101 of itself and the 1st embodiment is to have the cross valve 113 of the flow direction that switches cold-producing medium in the cold-producing medium peripheral passage.
Promptly, the air conditioner 106 of the 6th embodiment is identical with the air conditioner 101a of the 1st embodiment, have Linearkompressor 1b, the flow controller 57b, the 1st heat exchanger 111 and the 2nd heat exchanger 112 that form the cold-producing medium peripheral passage, and have the 101b of driven compressor portion that drives this Linearkompressor 1b.Here, the 1st heat exchanger 111 constitutes above-mentioned indoor set 114, and flow controller 57b, the 2nd heat exchange look 112, Linearkompressor 1b, cross valve 113 and the 101b of driven compressor portion constitute above-mentioned off-premises station 115.In addition, Linearkompressor 1a, the 101a of driven compressor portion, the flow controller 57a with refrigerating circulatory device (air conditioner) 101a that constitutes the 1st embodiment is identical respectively with flow controller 57b for above-mentioned Linearkompressor 1b, the 101b of driven compressor portion.
In addition, above-mentioned the 1st heat exchanger 111 is for being arranged at indoor indoor side heat exchanger, and it is equivalent to the 1st heat exchanger (evaporimeter) 53a among the air conditioner 101a that freezes of the 1st embodiment.Above-mentioned the 2nd heat exchanger 112 is for to be arranged at outdoor outdoor heat exchanger, and it is equivalent to the 2nd heat exchanger (condenser) 55a among the air conditioner 101a the 1st embodiment, that freeze.Here, above-mentioned indoor side heat exchanger 111 comprises: hair-dryer 111a, and this hair-dryer 111a is used to improve the ability of heat exchange; Temperature sensor 111b, this temperature sensor 111b measures temperature or its peripheral temperature of heat exchanger 111, and this temperature sensor 111b is equivalent to the 1st surroundings Temperature Detector 3 of the 1st embodiment.Above-mentioned outdoor heat exchanger 112 comprises: the hair-dryer 112a that is used to improve the ability of heat exchange, and temperature sensor 112b, this temperature sensor 112b measures temperature or its peripheral temperature of this heat exchanger 112, and this temperature sensor 112b is equivalent to the 2nd surroundings Temperature Detector 3 of the 1st embodiment.
In addition, in the 6th embodiment, in the refrigerant passage between above-mentioned the 1st heat exchanger 111 and the 2nd heat exchanger 112, compressor 1b and cross valve 113 are set.Promptly, in this air conditioner 106, the cold-producing medium that will pass through the 2nd heat exchanger 112 is drawn among the compressor 1b, the state that to supply with the 1st heat exchanger 111 from the cold-producing medium that compressor 1b discharges (promptly, the state that cold-producing medium flows in the direction of arrow A), and the cold-producing medium that has passed through the 1st heat exchanger 111 is drawn among the compressor 1b, and the state (that is, cold-producing medium flow along the arrow B direction state) that the cold-producing medium of discharging from compressor 1b is supplied with the 2nd heat exchanger 112 is switched by above-mentioned cross valve 113.
In addition, above-mentioned flow controller 57b is identical with the occasion of the 1st embodiment, the throttling action of the flow of the cold-producing medium that has throttling simultaneously and circulated; And the effect of automatically adjusting the valve (self regulating valve) of the flow of cold-producing medium.Promptly, flow controller 57b is under the state of cold-producing medium in cold-producing medium peripheral passage circulation, flow to the liquid refrigerant sent to evaporimeter from condenser carries out throttling and this liquid refrigerant is expanded, and supplies with the cold-producing medium of the necessary amount of evaporimeter under unnecessary, not enough situation.
Below action is described.
In the air conditioner 106 of the 6th embodiment, if Linearkompressor 1b is added drive current Cd from the 101b of driven compressor portion, then, carry out heat exchange by the 1st heat exchanger 111 of indoor set 114 and the 2nd heat exchanger 112 of off-premises station 115 in the circulation of cold-producing medium peripheral passage inner refrigerant.Thus, carry out indoor heating or refrigeration.
Such as, in the occasion of the warming operation that carries out air conditioner 116, by user's operation, above-mentioned cross valve 113 is set along the mode that the direction shown in the arrow A flows according to cold-producing medium.In this occasion, the circulation of the cold-producing medium by above-mentioned cold-producing medium peripheral passage, the 1st heat exchanger (indoor side heat exchanger) 111 is as condenser action, discharges heat.Thus, heat to indoor.
Otherwise in the occasion of the cooling operation that carries out air conditioner 116, by user's operation, above-mentioned cross valve 113 is set along the mode that the direction shown in the arrow B flows according to cold-producing medium.In this occasion, follow the circulation of the cold-producing medium of above-mentioned cold-producing medium peripheral passage, the 1st heat exchanger (indoor side heat exchanger) 111 moves as evaporimeter, absorbs the heat of ambient air.Thus, freeze to indoor.
Like this, in the air conditioner 106 of the 6th embodiment, because it is identical with the air conditioner 101 of the 1st embodiment, not only according to indoor temperature (environment temperature of the 1st heat exchanger 111), but also calculate the volume internal circulating load Vco of the desired cold-producing medium of this air conditioner, so can make the calculated value of the volume internal circulating load of desired cold-producing medium become the value that is more suitable for operating condition according to outdoor temperature (environment temperature of the 2nd heat exchanger 12).
That is, have following effect, can avoid the operating condition of air conditioner the indoor obstruction comfortableness of excessively freezing or excessively heating, such as, can make indoor temperature become design temperature in the shorter time.
In addition, in the air conditioner 106 of the 6th embodiment,,, can carry out more high efficiency running so in the running of air conditioner, do not use the electric power of waste owing to avoid hindering the operating condition of comfortableness as described above.
(the 7th embodiment)
Fig. 8 is the block diagram of the refrigerating box of explanation the 7th embodiment of the present invention.
The refrigerating box 107 of the 7th embodiment adopts the refrigerating circulatory device 101 of the 1st embodiment, identical with the 1st embodiment, have Linearkompressor 1c, the flow controller 57c, the 1st heat exchanger 122 and the 2nd heat exchanger 121 that form the cold-producing medium peripheral passage, and have the 101c of driven compressor portion that drives above-mentioned Linearkompressor 1c.
That is, above-mentioned flow controller 57c, Linearkompressor 1c and the 101c of driven compressor portion are identical with flow controller 57a, Linearkompressor 1a and the 101a of driven compressor portion of the 1st embodiment.
In addition, above-mentioned the 2nd heat exchanger 121 is the condenser of discharges heat in atmosphere, and it is equivalent to the 2nd heat exchanger (condenser) 55a among the air conditioner 101a that freezes of the 1st embodiment.The refrigerator evaporator of above-mentioned the 1st heat exchanger 122 for refrigerating box inside is cooled off, it is equivalent to the 1st heat exchanger (evaporimeter) 53a among the air conditioner 101a the 1st embodiment, that freeze.Here, above-mentioned refrigerator evaporator 122 comprises the hair-dryer 122a of the ability that is used to improve heat exchanger and the temperature sensor 122b that detects the temperature in this refrigerating box, and this temperature sensor 122b is equivalent to the 1st surroundings Temperature Detector 3 of the 1st embodiment.
Below action is described.
In the refrigerating box 107 of the 7th embodiment, if Linearkompressor 1c is added drive current Cd from the 101c of driven compressor portion, then in the inside of cold-producing medium peripheral passage, cold-producing medium circulates in the direction of arrow C, carries out heat exchange by condenser 121 and refrigerator evaporator 122.Thus, the inside of refrigerating chamber is cooled off.
That is, by flow controller 57c, the flow that becomes the cold-producing medium of liquid state by the 2nd heat exchanger (condenser) 121 is carried out throttling control, thus, this cold-producing medium expands, and forms the refrigerating fluid of low temperature.Then, if the liquid refrigerant of low temperature is sent in the 1st heat exchanger (refrigerator evaporator) 122, then in the 1st heat exchanger (refrigerator evaporator) 122, the cooling of refrigerating chamber is carried out in the evaporation of refrigerant of low temperature liquid.At this moment, in heat exchanger 122, send into air in the refrigerating chamber forcibly, in heat exchanger 122, carry out heat exchange expeditiously by pressure fan 122a.In addition, at this moment,, detection signal is exported to above-mentioned compressor drive division 101c by the temperature in the temperature sensor 122b detection case.The 101c of this driven compressor portion calculates the volume internal circulating load Vco of the desired cold-producing medium of refrigerating circulatory device according to the temperature information that is detected by temperature sensor 122b, according to the volume internal circulating load of the cold-producing medium that has calculated Linearkompressor 1c is driven control.
Like this, in the refrigerating box 107 of the 7th embodiment, because it is identical with the air conditioner 101 of the 1st embodiment, according to the temperature in the refrigerating box (environment temperature of the 1st heat exchanger 122), calculate the volume internal circulating load Vco of the desired cold-producing medium of this refrigerating box, so can make the calculated value of the volume internal circulating load of desired cold-producing medium become the value that is more suitable for operating condition.
That is, in the 7th embodiment, have following effect, that is, can avoid the relatively poor operating condition of efficient cold excessively in the refrigerating box, such as, can in the shorter time, make the temperature in the refrigerating box become design temperature.
(the 8th embodiment)
Fig. 9 is the block diagram of the hot water supply apparatus of explanation the 8th embodiment of the present invention.
The hot water supply apparatus 108 of the 8th embodiment comprises: refrigerating circulatory device 142,142 pairs of water of being supplied with of this refrigerating circulatory device heat the back and discharge hot water; Hot-water storage groove 141, this hot-water storage groove 141 is stored the hot water of discharging from refrigerating circulatory device 142.
Above-mentioned refrigerating circulatory device 142 is identical with the refrigerating circulatory device 101 of the 1st embodiment, comprise Linearkompressor 1d, the flow controller 57d, the 1st heat exchanger the 132, the 2nd heat exchanger 135 that form the cold-producing medium peripheral passage, and have the 101d of driven compressor portion that drives above-mentioned Linearkompressor 1d.
That is, above-mentioned flow controller 57d, Linearkompressor 1d and the 101d of driven compressor portion are that 101a is identical for flow controller 57a, Linearkompressor 1a, driven compressor portion with the 1st embodiment.
Above-mentioned the 2nd heat exchanger 135 is a water heat exchanger, and it heats the water of supplying with refrigerating circulatory device 142, and it is equivalent to the 2nd heat exchanger (condenser) 55a of the air conditioner 101a that freezes of the 1st embodiment.Above-mentioned the 1st heat exchanger 132 is the air heat exchanger that absorbs heat from peripheral atmosphere, is equivalent to the 1st heat exchanger (evaporimeter) 53a of air conditioner 101a the 1st embodiment, that freeze.Here, above-mentioned water heat exchanger 135 comprises temperature sensor 135a, and this temperature sensor 135a detects the temperature of heated water (hot water), and this temperature sensor 135a is equivalent to the 2nd surroundings Temperature Detector 5 of the 2nd embodiment.Above-mentioned air heat exchanger 132 comprises hair-dryer 132a, and this hair-dryer 132a is used to improve the ability of heat exchange; Temperature sensor 132b, this temperature sensor 132b detects this peripheral temperature.This temperature sensor 132b is equivalent to the 1st surroundings Temperature Detector 3 of the 1st embodiment.
In addition, in the drawings, label 131 expression refrigerant pipes, this refrigerant pipe 131 make above-mentioned cold-producing medium along the cold-producing medium peripheral passage circulation that is formed by the 1st heat exchanger 132, flow controller 57d and the 2nd heat exchanger 135.On this refrigerant pipe 131, connect shunt valve (defrosting bypass) 133, this shunt valve will make a circulation the 2nd heat exchanger 135 and flow controller 57d from the cold-producing medium that compressor 1d discharges and be supplied in the 1st heat exchanger 132, and the part of this shunt valve 133 is provided with valve (defrosting bypass valve) 134.
Above-mentioned hot-water storage groove 141 comprises the hot-water storage case 138 of storage of water or hot water.On the water inlet 138c of this hot-water storage case 138, be connected with pipe (feed pipe) 140, this the pipe 140 from the outside to the private water supply of this hot-water storage case 138, be connected with pipe (bathtub hot water supply pipe) 140 on the hot water outlet 138d of above-mentioned hot-water storage case 138, this pipe 140 is supplied with hot water from this hot-water storage case 138 to bathtub (bathroom).In addition, be connected with hot water supply pipe 139 on the water entrance 138a of above-mentioned hot-water storage case 138, the hot water supply that this hot water supply pipe 139 will be stored in this case 138 is arrived outside.
Water heat exchanger 135 in above-mentioned hot-water storage case 138 and the refrigerating circulatory device 142 is by pipe 136a, and 136b, 146a and 146b connect, and forms the peripheral passage of water between hot-water storage case 138 and water heat exchanger 135.
Here, water pipe 136b is the pipe that supplies water to water heat exchanger 135 from hot-water storage case 138, and the one end is connected with the delivery port 138b of hot-water storage case 138, and the other end is connected with the entry side pipe 146b of water heat exchanger 136b by blank area 143b.In addition, at the distolateral water that is used to discharge in the hot-water storage case 138 or the draining valve 144 of hot water of being equipped with of this pipe 136b.Above-mentioned water pipe 136a is for turning back to the pipe of hot-water storage case 138 with water from water heat exchanger 135, and the one end is connected with the intake-outlet 138a of this hot-water storage case 138, and its other end passes through coupling part 143a and is connected with the discharge side pipe 146a of water heat exchanger 135.
In addition, the part that enters side pipe 146b of water heat exchanger 135 is provided with and makes the pump 137 of water in above-mentioned water circulation path inner loop.
Below action is described.
If add drive current Cd from 101 couples of Linearkompressor 1d of driven compressor portion, Linearkompressor 1d drives, then the high temperature refrigerant by this Linearkompressor 1d compression circulates along arrow D direction,, supplies with the 2nd heat exchangers (water heat exchanger) 135 by refrigerant pipe 131 that is.In addition, if the pump of water circulation path 137 drives, then supply water to the 2nd heat exchanger 135 from hot-water storage case 138.
So, in the 2nd heat exchanger (water heat exchanger) 135, carrying out heat exchange at cold-producing medium and between the water of hot-water storage case 138 supplies, heat is shifted to water from cold-producing medium.That is, the water of having supplied with is heated, heated water (hot water) supplies to hot-water storage case 138.At this moment, the temperature of heated water (hot water) monitors by condensation temperature sensor 135a.
In addition, in the 2nd heat exchanger (water heat exchanger) 135, cold-producing medium is by above-mentioned heat exchange condensation, the flow of the liquid refrigerant of condensation carries out throttling control by flow controller 57d, thus, this liquid refrigerant expands, and is sent to the 1st heat exchanger (air heat exchanger) 132.In this hot water supply apparatus 108, the 1st heat exchanger (air heat exchanger) 132 is as evaporimeter.That is, this air heat exchanger 132 absorbs heat from the extraneous gas of sending into by hair-dryer 132b, makes the refrigerating fluid evaporation of low temperature.At this moment, the temperature of the peripheral atmosphere of above-mentioned air heat exchanger 132 is monitored by temperature sensor 132b.
In addition, in refrigerating circulatory device 142, tied white occasion on the 1st heat exchanger (air heat exchanger) 132, defrosting bypass valve 134 is opened, and the cold-producing medium of high temperature is supplied with the 1st heat exchanger (air heat exchanger) 132 by bypass 133.Thus, the 2nd heat exchanger (air heat exchanger) 132 is defrosted.
Also have, in hot-water storage groove 141, the water heat exchanger 135 from refrigerating circulatory device 108 is supplied with hot water by pipe 146a and 136a, and the hot-water storage that is supplied to is in hot-water storage case 138.Hot water in this hot-water storage case 138 supplies to the outside by hot-water line 139 as required.Particularly, in occasion from hot water to bathtub that supply with, the hot water in the hot-water storage case supplies to bathtub by bathtub with heat supply water pipe 140.
Have, the water in hot-water storage case 138 or the storage capacity of hot water pass through feed pipe 140 supplementing water less than a certain amount of occasion from the outside again.
Like this, in the hot water supply apparatus 108 of this 8th embodiment 8, because it is identical with the air conditioner of the 1st embodiment, the temperature of the hot water of supplying with from hot water supply apparatus 108 that detects according to temperature sensor 135a, calculating the volume internal circulating load Vco of the desired cold-producing medium of refrigerating circulatory device of hot water supply apparatus, is the value that is more suitable for the operating condition of hot water supply apparatus so can make the calculated value of the volume internal circulating load of desired cold-producing medium.
That is, have following effect, can avoid operating condition that hot water supply apparatus too heats water, that efficient is relatively poor, such as, can in the shorter time, make the temperature of the hot water of supplying with from hot water supply apparatus become design temperature.
(the 9th embodiment)
Figure 10 is the block diagram of the cryogenic refrigerator of explanation the 9th embodiment of the present invention.
The utmost point low-temperature freezing facilities 109 of the 9th embodiment has refrigerating chamber, this refrigerating chamber inside can be cooled to utmost point low-temperature condition (below 50 ℃), in the article (cooling object) that adopt this utmost point low-temperature freezing facilities 109 to cool off, included low temperature that conducting element (the electromagnetic circuit elements of resistance, coil, magnet etc.), infrared ray sensor use therapeutic medical article with reference to electronic unit, blood or the internal organ of portion etc., and the frozen food of freezing tuna etc.
Make electronic unit be in utmost point low-temperature condition, its purpose is to improve efficiency of movement, or improve to remove the sensitivity of thermal noise, in food etc., carries fresh food or carry out freshness to keep or carry out drying.
In addition, chilling temperature at this utmost point low-temperature freezing facilities is being used for the superconductive occasion of high temperature, be set in 50～100K (K: the utmost point low-temperature condition in scope absolute temperature), be used for common superconductive occasion, be set in the utmost point low-temperature condition in the scope of 0～50K.In addition, in the occasion of the fresh maintenance that is used for food etc., a little less than the chilling temperature of this utmost point low-temperature freezing facilities is set in-50 ℃ (Celsius).
Be specifically described below.
The utmost point low-temperature freezing facilities 109 of the 9th embodiment adopts the kind of refrigeration cycle 101 of the 1st embodiment, identical with the 1st embodiment, comprise Linearkompressor 1e, the flow controller 57e, the 1st heat exchanger 152 and the 2nd heat exchanger 151 that form the cold-producing medium peripheral passage, and have the 101e of driven compressor portion that drives above-mentioned Linearkompressor 1e.
That is, above-mentioned flow controller 57e, Linearkompressor 1e and the 101e of driven compressor portion are identical with flow controller 57e, Linearkompressor 1a and the 101a of driven compressor portion of the 1st embodiment.
In addition, above-mentioned the 2nd heat exchanger 151 is the radiator of discharges heat in atmosphere, and it is equivalent to the condenser 55a of the air conditioner 101a that freezes of the 1st embodiment.The regenerator of above-mentioned the 1st heat exchanger 152 for refrigerating chamber inside is cooled off, it is equivalent to the evaporimeter 53a of air conditioner 101a the 1st embodiment, that freeze.Here, above-mentioned radiator 152 comprises: hair-dryer 152a, and this hair-dryer 152a is used to improve the ability of heat exchange; Temperature sensor 152b, this temperature sensor 152b detects the temperature in the refrigerating chamber, and this temperature sensor 152b is equivalent to the 1st surroundings Temperature Detector 3 of the 1st embodiment.
Below action is described.
In the utmost point low-temperature freezing facilities 109 of the 9th embodiment, if Linearkompressor 1e is added drive current Cd from the 101e of driven compressor portion, then in inside, cold-producing medium peripheral passage, cold-producing medium circulates in the direction of arrow E, carries out heat exchange by radiator 151 and regenerator 152.Thus, refrigerating chamber is cooled off.
That is, with flow controller 57e the flow of the cold-producing medium of the shape that is in a liquid state is carried out throttling control in the 2nd heat exchanger (radiator) 151, this cold-producing medium expands, and forms the refrigerating fluid of low temperature.In addition, if the liquid refrigerant of low temperature is sent to the 1st heat exchanger (regenerator) 152, then in the 1st heat exchanger (regenerator) 152, the evaporation of the refrigerating fluid of low temperature is cooled off refrigerating chamber.At this moment, forcibly the air in the refrigerating chamber is sent to this regenerator 152, in regenerator 152, carries out heat exchange expeditiously by hair-dryer 152a.In addition, at this moment,, detection signal is exported to above-mentioned compressor drive division 101e by the temperature in the temperature sensor 152b detection refrigerating chamber.The 101e of driven compressor portion calculates the volume internal circulating load Vco of the desired cold-producing medium of refrigerating circulatory device according to the temperature information that is detected by temperature sensor 152e, according to the volume internal circulating load of calculated cold-producing medium Linearkompressor 1e is driven control.
Like this, in the utmost point low-temperature freezing facilities 109 of the 9th embodiment, because it is identical with the air conditioner 101 of the 1st embodiment, according to the volume internal circulating load Vco of the desired cold-producing medium of the temperature in the refrigerating chamber (that is, the temperature of freezing object) calculating refrigerating circulatory device, so have following effect, promptly, the calculated value that can make the volume internal circulating load of desired cold-producing medium is the value that is more suitable for the operating condition of utmost point low-temperature freezing facilities, thus, can control the temperature of freezing object accurately.
In addition, in above-mentioned the 6th～9 embodiment, driven compressor portion adopts the identical type of the 101a of driven compressor portion with the refrigerating circulatory device 101 of the 1st embodiment, but, the driven compressor portion of the 6th～9 embodiment is not limited to the type of the 1st embodiment, and it also can adopt any (the compression trifoliate orange drive division 102a～105a) among the 2nd～5 embodiment.
Effect of the present invention
As above-mentioned, because the present invention's's (claim 1) refrigerating circulatory device relates to following refrigerating circulatory device, it comprises: the 1st heat exchanger and the 2nd heat exchanger that form the peripheral passage of cold-producing medium; Linearkompressor, this Linearkompressor has piston and makes the linear motor of this reciprocating motion of the pistons, follow the reciprocating motion of this piston, make the cold-producing medium circulation in the above-mentioned peripheral passage, it is characterized in that, this refrigerating circulatory device comprises: reverser, and this reverser produces the alternating current that drives above-mentioned linear motor; Actual cycle amount test section, this actual cycle amount test section detects the reciprocating motion that above-mentioned piston is followed in expression, the circulating mass of refrigerant of the reality of the volume of Linearkompressor unit interval and the cold-producing medium of discharging or sucking; Target circulation amount leading-out portion, this target circulation amount leading-out portion is according to two or one the peripheral temperature and the target temperature of a setting in relative at least this two heat-exchanger in above-mentioned the 1st heat exchanger and the 2nd heat exchanger, the target circulating mass of refrigerant of the volume of above-mentioned Linearkompressor unit interval of induced representation and the cold-producing medium that should discharge or suck; Control part, this control part is controlled above-mentioned reverser, make the circulating mass of refrigerant of above-mentioned reality and the difference between the above-mentioned target circulating mass of refrigerant reduce, so identical, can adopt the control of refrigerating capacity of the refrigerating circulatory device of Linearkompressor expeditiously according to the volume internal circulating load of cold-producing medium with the rotary-type refrigerating circulatory device of adopt.
Because the present invention's (claim 2) relates to the described refrigerating circulatory device of claim 1, it is characterized in that it comprises: stroke detection portion, the trip test section detects the haul distance of the piston that moves back and forth; The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth; Above-mentioned actual cycle amount test section calculates the volume that 1 time of following piston moves back and forth the cold-producing medium of discharging or sucking according to above-mentioned detected haul distance and above-mentioned detected upper dead center position, the multiplying of the frequency by the above-mentioned alternating current that volume and above-mentioned reverser produced that has calculated, obtain the circulating mass of refrigerant of above-mentioned reality, so can expeditiously the refrigerating capacity of refrigerating circulatory device be controlled not adopting under the situation of measuring the volume internal circulating load.
Because the present invention's (claim 3) relates to the described refrigerating circulatory device of claim 2, it is characterized in that it comprises: discharge pressure is inferred portion, this discharge pressure is inferred the temperature of portion according to the cold-producing medium of the heat exchanger that makes condensation of refrigerant of cold-producing medium discharge side in the above-mentioned peripheral passage, that be positioned at Linearkompressor, infers the pressure of the cold-producing medium of above-mentioned Linearkompressor discharge; Suction pressure is inferred portion, and this suction pressure is inferred the pressure of portion according to the cold-producing medium of the above-mentioned Linearkompressor suction of temperature estimation of the cold-producing medium of the heat exchanger that makes the cold-producing medium evaporation of cold-producing medium in the above-mentioned peripheral passage, that be positioned at Linearkompressor suction side; Above-mentioned actual cycle amount test section obtains by the pressure that adopts the discharging refrigerant of being inferred according to the pressure and the quilt of above-mentioned suction cold-producing medium of having inferred, the computing of the maximum pressure of the cold-producing medium of above-mentioned peripheral passage and the pressure ratio of minimum pressure and above-mentioned detected haul distance and above-mentioned detected upper dead center position, obtain 1 reciprocating motion following above-mentioned piston and the volume of the cold-producing medium of discharging or sucking, even so for following the operating condition pressure state to change, the discharge pressure of cold-producing medium and the pressure ratio of suction pressure change such refrigerating circulatory device, still can control the refrigerating capacity of refrigerating circulatory device according to the volume internal circulating load high efficiency of cold-producing medium.
Because the present invention's's (claim 4) refrigerating circulatory device relates to following refrigerating circulatory device, it comprises: the 1st heat exchanger and the 2nd heat exchanger that form the peripheral passage of cold-producing medium; Linearkompressor, this Linearkompressor has piston and makes the linear motor of this reciprocating motion of the pistons, reciprocating motion by this piston circulates the cold-producing medium in the above-mentioned peripheral passage, it is characterized in that this refrigerating circulatory device comprises: reverser, this reverser produces the alternating current that drives above-mentioned linear motor; Actual cycle amount test section, this actual cycle amount test section detect expression because the reciprocating motion Linearkompressor unit interval of above-mentioned piston discharges or the circulating mass of refrigerant of the reality of the weight of the cold-producing medium of suction; Target circulation amount leading-out portion, this target circulation amount leading-out portion is according to two in above-mentioned the 1st heat exchanger and the 2nd heat exchanger or one 's peripheral temperature, and the target circulating mass of refrigerant of the weight of in these two heat exchangers and above-mentioned Linearkompressor unit interval of target temperature induced representation of setting and the cold-producing medium that should discharge or suck at least relatively; Control part, this control part is controlled above-mentioned reverser, make the circulating mass of refrigerant of above-mentioned reality and the difference between the above-mentioned target circulation amount reduce, so can be corresponding to the temperature of the reality in the room that freezes and the temperature difference of its target temperature, expeditiously the refrigerating capacity of refrigerating circulatory device is controlled, in addition, owing to realize the refrigerating capacity of this refrigerating circulatory device, so better response can be arranged, stably carry out the control of refrigerating capacity according to weight internal circulating load with the more closely-related cold-producing medium of load of this refrigerating circulatory device.
Because the present invention's (claim 5) relates to the described refrigerating circulatory device of claim 4, it is characterized in that it comprises: stroke detection portion, the trip test section detects the haul distance of the piston that moves back and forth; The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth; Discharging refrigerant Density Detection portion, this discharging refrigerant Density Detection portion is detected from the density of the cold-producing medium of above-mentioned Linearkompressor discharge, above-mentioned actual cycle amount test section is according to above-mentioned detected haul distance and above-mentioned detected upper dead center position, the volume of the cold-producing medium that calculating is discharged by 1 reciprocating motion of above-mentioned piston, according to this volume that calculates, above-mentioned detected density, the frequency of the alternating current that above-mentioned reverser produced is obtained with the weight of unit interval by the cold-producing medium of Linearkompressor discharge, so can not adopt the sensor of the weight internal circulating load of measuring cold-producing medium, and only adopt the sensor of the density of measuring discharging refrigerant to carry out effective control based on the refrigerating capacity of the refrigerating circulatory device of the weight internal circulating load of cold-producing medium.
Because the present invention's (claim 6) relates to the described refrigerating circulatory device of claim 5, it is characterized in that it comprises: discharge temperature test section, this discharge temperature test section detect from the temperature of the cold-producing medium of above-mentioned Linearkompressor discharge; Discharge pressure test section, this discharge pressure test section detect from the pressure of the cold-producing medium of above-mentioned Linearkompressor discharge; Above-mentioned discharging refrigerant Density Detection portion is according to the temperature and the pressure of above-mentioned detected cold-producing medium of discharging from Linearkompressor, the density of the cold-producing medium that derivation is discharged from above-mentioned Linearkompressor is so can carry out effective control based on the refrigerating capacity weight internal circulating load, refrigerating circulatory device of cold-producing medium under the situation of the sensor of the density that does not adopt the mensuration cold-producing medium.
Because the present invention's (claim 7) relates to the described refrigerating circulatory device of claim 4, it is characterized in that it comprises: stroke detection portion, the trip test section detects the haul distance of the piston that moves back and forth; The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth; Suck the refrigerant density test section, this suction refrigerant density test section detects the density that is drawn into the cold-producing medium in the above-mentioned Linearkompressor; Above-mentioned actual cycle amount test section is according to above-mentioned detected haul distance and above-mentioned detected upper dead center position, the volume of the cold-producing medium that moves back and forth for 1 time of above-mentioned piston and discharge is followed in calculating, according to this calculated volume, the density of above-mentioned detected cold-producing medium and the frequency of the alternating current that above-mentioned reverser produced are obtained the weight that time per unit is drawn into the cold-producing medium in the Linearkompressor, so can be under the situation of the sensor that does not adopt the gravimetry internal circulating load only adopt the sensor of measuring the density that sucks cold-producing medium, carry out based on the weight internal circulating load of cold-producing medium, the high efficiency control of the refrigerating capacity of refrigerating circulatory device.
Because the present invention's (claim 8) relates to the described refrigerating circulatory device of claim 7, it is characterized in that it comprises: the inlet temperature test section, this inlet temperature test section detects the temperature that is drawn into the cold-producing medium in the above-mentioned Linearkompressor; The suction pressure test section, this suction pressure test section detects the pressure that is drawn into the cold-producing medium in the above-mentioned Linearkompressor; Above-mentioned suction refrigerant density test section is according to the above-mentioned detected temperature and pressure that is drawn into the cold-producing medium in the Linearkompressor, obtain the density that is drawn into the cold-producing medium in the above-mentioned Linearkompressor, so can under the situation that does not adopt the sensor of measuring the density that sucks cold-producing medium, carry out high efficiency control based on the refrigerating capacity weight internal circulating load, refrigerating circulatory device of cold-producing medium.
Because the present invention's (claim 9) relates to the described refrigerating circulatory device of claim 8, it is characterized in that it comprises: the refrigerant temperature detector, this refrigerant temperature detector detects as the temperature of the cold-producing medium of the evaporimeter of the heat exchanger that the makes cold-producing medium evaporation saturation temperature as the cold-producing medium that is drawn into above-mentioned Linearkompressor cold-producing medium in the above-mentioned peripheral passage, that be arranged in Linearkompressor suction side; The degree of superheat is inferred portion, and this degree of superheat is inferred portion and inferred the degree of superheat as the cold-producing medium of the temperature difference that is drawn into the temperature of the cold-producing medium in the above-mentioned Linearkompressor and saturation temperature according to the operating condition of above-mentioned Linearkompressor; Above-mentioned inlet temperature test section carries out the addition calculation to the temperature of the cold-producing medium in the above-mentioned detected evaporimeter and the degree of superheat of above-mentioned cold-producing medium of having inferred, obtain the temperature that sucks the cold-producing medium in the above-mentioned Linearkompressor, so the sensor that does not adopt the sensor of measuring the density that sucks cold-producing medium and measure the temperature of suction cold-producing medium just can carry out the high efficiency control based on the refrigerating capacity weight internal circulating load, refrigerating circulatory device of cold-producing medium.
Because the present invention's (claim 10) relates to a kind of air conditioner, this air conditioner comprises any one the described refrigerating circulatory device in the claim 1～9, it is characterized in that above-mentioned the 1st heat exchanger is an outdoor heat exchanger, above-mentioned the 2nd heat exchanger is an indoor side heat exchanger, so have the running that can prevent cold or overheated obstruction comfortableness, such as, can in the shorter time, make indoor temperature become the effect of design temperature.In addition, in the running of above-mentioned such air conditioner, owing to do not adopt unhelpful electric power, so can carry out the more high efficiency running of air conditioner.
Because the present invention's (claim 11) relates to a kind of refrigerating box, this refrigerating box comprises any one the described refrigerating circulatory device in the claim 1～9, it is characterized in that above-mentioned the 1st heat exchanger is the condenser of discharges heat; Above-mentioned the 2nd heat exchanger is evaporimeter to cooling off in the case, can avoid making the relatively poor operating condition of the cold excessively efficient in refrigerating box inside so have, such as, can when shorter, the temperature in the chien shih refrigerating box become design temperature.
Because the present invention's (claim 12) relates to a kind of hot water supply apparatus, this hot water supply apparatus comprises any one the described refrigerating circulatory device in the claim 1～9, it is characterized in that the hopper that it comprises storage of water; The water heat exchanger that above-mentioned the 1st heat exchanger heats for the water to above-mentioned hopper; Above-mentioned the 2nd heat exchanger is the air heat exchanger that absorbs heat from peripheral atmosphere, so have following effect, promptly, avoid hot water supply apparatus to the relatively poor operating condition of the superheated efficient of water, such as, can be when shorter the temperature of the hot water supplied with from hot water supply apparatus of chien shih become design temperature.
Because the present invention's (claim 13) relates to a kind of utmost point low-temperature freezing facilities, this cryogenic refrigerator comprises any one the described refrigerating circulatory device in the claim 1～9, it is characterized in that it comprises refrigerating chamber, above-mentioned the 1st heat exchanger is the radiator of discharges heat, above-mentioned the 2nd heat exchanger is for the regenerator to cooling off in the above-mentioned refrigerating chamber, so have the effect that can obtain the higher temperature controlled cryogenic refrigerator of precision.

Claims (13)

1. refrigerating circulatory device, this refrigerating circulatory device comprises:
Form the 1st heat exchanger and the 2nd heat exchanger of the peripheral passage of cold-producing medium;
Linearkompressor, this Linearkompressor have piston and make the linear motor of this reciprocating motion of the pistons, make cold-producing medium circulation in the above-mentioned peripheral passage by the reciprocating motion of this piston, it is characterized in that this refrigerating circulatory device comprises:
Reverser, this reverser produces the alternating current that drives above-mentioned linear motor;
Actual cycle amount test section, this actual cycle amount test section detect the reciprocating motion of expression owing to above-mentioned piston, the circulating mass of refrigerant of the reality of the volume of the cold-producing medium that the Linearkompressor unit interval discharges or sucks;
Target circulation amount leading-out portion, the target temperature that this target circulation amount leading-out portion is set according to both sides in above-mentioned the 1st heat exchanger and the 2nd heat exchanger or a side's peripheral temperature and the side in relative at least this two heat-exchanger, the target circulating mass of refrigerant of the volume of the cold-producing medium that the above-mentioned Linearkompressor unit interval of induced representation should be discharged or suck; With
Control part, this control part is controlled above-mentioned reverser, makes the circulating mass of refrigerant of above-mentioned reality and the difference between the above-mentioned target circulating mass of refrigerant reduce.
2. refrigerating circulatory device according to claim 1 is characterized in that it comprises:
Stroke detection portion, the trip test section detects the haul distance of the piston that moves back and forth;
The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth;
Above-mentioned actual cycle amount test section is according to above-mentioned detected haul distance and above-mentioned detected upper dead center position, calculating is by the volume that for 1 time of piston moves back and forth the cold-producing medium of discharging or sucking, the circulating mass of refrigerant of above-mentioned reality is obtained in the multiplying of the frequency of the alternating current that volume and above-mentioned reverser produced that is gone out by aforementioned calculation.
3. refrigerating circulatory device according to claim 2 is characterized in that it comprises:
Discharge pressure is inferred portion, this discharge pressure is inferred the temperature of portion according to the cold-producing medium of cold-producing medium discharge in the above-mentioned peripheral passage, that be positioned at Linearkompressor heat exchanger side, that make condensation of refrigerant, infers the pressure of the cold-producing medium of above-mentioned Linearkompressor discharge;
Suction pressure is inferred portion, this suction pressure is inferred the temperature of portion according to the cold-producing medium of heat exchanger cold-producing medium in the above-mentioned peripheral passage, that be positioned at Linearkompressor suction side, that make the cold-producing medium evaporation, infers the pressure of the cold-producing medium of above-mentioned Linearkompressor suction;
Above-mentioned actual cycle amount test section is by adopting according to the maximum pressure of the pressure cold-producing medium that obtain, above-mentioned peripheral passage of the pressure of above-mentioned suction cold-producing medium of being inferred and the discharging refrigerant of being inferred and the pressure ratio of minimum pressure and computing according to above-mentioned detected haul distance and above-mentioned detected upper dead center position, obtains by above-mentioned piston 1 time and moves back and forth and discharge or the volume of the cold-producing medium of suction.
4. refrigerating circulatory device, this refrigerating circulatory device comprises the 1st heat exchanger and the 2nd heat exchanger of the peripheral passage that forms cold-producing medium; Linearkompressor, this Linearkompressor have piston and make the linear motor of this reciprocating motion of the pistons, make cold-producing medium circulation in the above-mentioned peripheral passage by the reciprocating motion of this piston, it is characterized in that this refrigerating circulatory device comprises:
Reverser, this reverser produces the alternating current that drives above-mentioned linear motor;
Actual cycle amount test section, this actual cycle amount test section detect the reciprocating motion of expression by above-mentioned piston, the circulating mass of refrigerant of the reality of the weight of the cold-producing medium that the Linearkompressor unit interval discharges or sucks;
Target circulation amount leading-out portion, this target circulation amount leading-out portion is according to both sides or a side peripheral temperature and the target temperature that the side in relative at least these two heat exchangers sets in above-mentioned the 1st heat exchanger and the 2nd heat exchanger, the target circulating mass of refrigerant of the weight of the cold-producing medium that the above-mentioned Linearkompressor unit interval of induced representation should be discharged or suck; With
Control part, this control part is controlled above-mentioned reverser, makes the circulating mass of refrigerant of above-mentioned reality and the difference between the above-mentioned target circulation amount reduce.
5. refrigerating circulatory device according to claim 4 is characterized in that it comprises:
Stroke detection portion, the trip test section detects the haul distance of the piston that moves back and forth;
The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth;
Discharging refrigerant Density Detection portion, this discharging refrigerant Density Detection portion are detected from the density of the cold-producing medium of above-mentioned Linearkompressor discharge;
Above-mentioned actual cycle amount test section is according to above-mentioned haul distance that is detected and the above-mentioned upper dead center position that is detected, calculating is by the volume that for 1 time of above-mentioned piston moves back and forth the cold-producing medium of discharging, and obtains the weight of the cold-producing medium that the above-mentioned unit interval discharges from Linearkompressor according to the frequency of this volume that calculates, above-mentioned detected density, alternating current that above-mentioned reverser produced.
6. refrigerating circulatory device according to claim 5 is characterized in that it comprises:
Discharge temperature test section, this discharge temperature test section detect from the temperature of the cold-producing medium of above-mentioned Linearkompressor discharge;
Discharge pressure test section, this discharge pressure test section detect from the pressure of the cold-producing medium of above-mentioned Linearkompressor discharge;
Above-mentioned discharging refrigerant Density Detection portion is according to the temperature and the pressure of above-mentioned detected cold-producing medium of discharging from Linearkompressor, derives the density of the cold-producing medium of discharging from above-mentioned Linearkompressor.
7. refrigerating circulatory device according to claim 4 is characterized in that it comprises:
Stroke detection portion, the trip test section detects the haul distance of the piston that moves back and forth;
The upper dead center position test section, this upper dead center position test section detects the upper dead center position of the piston that moves back and forth;
Suck the refrigerant density test section, this sucks the refrigerant density test section and detects the density that sucks the cold-producing medium in the above-mentioned Linearkompressor;
Above-mentioned actual cycle amount test section is according to above-mentioned haul distance that is detected and the above-mentioned upper dead center position that is detected, the volume that for 1 time of above-mentioned piston moves back and forth the cold-producing medium that sucks is followed in calculating, according to this calculated volume, the density of the above-mentioned cold-producing medium that is detected and the frequency of the alternating current that above-mentioned reverser produced are obtained the weight that is drawn into the cold-producing medium in the Linearkompressor with the unit interval.
8. refrigerating circulatory device according to claim 7 is characterized in that it comprises:
The inlet temperature test section, this inlet temperature test section detects the temperature that is drawn into the cold-producing medium in the above-mentioned Linearkompressor;
The suction pressure test section, this suction pressure test section detects the pressure that is drawn into the cold-producing medium in the above-mentioned Linearkompressor; With
Above-mentioned suction refrigerant density test section is obtained the density that is drawn into the cold-producing medium in the above-mentioned Linearkompressor according to above-mentioned temperature and pressure that be detected, that be drawn into the cold-producing medium in the Linearkompressor.
9. refrigerating circulatory device according to claim 8 is characterized in that it comprises:
The refrigerant temperature detector, this refrigerant temperature detector detects as the temperature of the cold-producing medium of the evaporimeter of the heat exchanger that the makes cold-producing medium evaporation saturation temperature as the cold-producing medium that is drawn into above-mentioned Linearkompressor cold-producing medium in the above-mentioned peripheral passage, that be arranged in Linearkompressor suction side;
The degree of superheat is inferred portion, and this degree of superheat is inferred the operating condition of portion according to above-mentioned Linearkompressor, infers the degree of superheat as the cold-producing medium of the temperature difference that is drawn into the temperature of the cold-producing medium in the above-mentioned Linearkompressor and saturation temperature; With
Above-mentioned inlet temperature test section carries out the addition calculation to the temperature of the cold-producing medium in the above-mentioned evaporimeter that has detected and the degree of superheat of above-mentioned cold-producing medium of having inferred, obtains the temperature that sucks the cold-producing medium in the above-mentioned Linearkompressor.
10. air conditioner, this air conditioner comprises any one the described refrigerating circulatory device in the claim 1～9, it is characterized in that:
Above-mentioned the 1st heat exchanger is an outdoor heat exchanger;
Above-mentioned the 2nd heat exchanger is an indoor side heat exchanger.
11. a refrigerating box, this refrigerating box comprise any one the described refrigerating circulatory device in the claim 1～9, it is characterized in that:
Above-mentioned the 1st heat exchanger is the condenser of discharges heat;
Above-mentioned the 2nd heat exchanger is the evaporimeter to cooling off in the case.
12. a hot water supply apparatus, this hot water supply apparatus comprise any one the described refrigerating circulatory device in the claim 1～9, it is characterized in that:
It comprises the hopper of storage of water;
The water heat exchanger that above-mentioned the 1st heat exchanger heats for the water to above-mentioned hopper;
Above-mentioned the 2nd heat exchanger is the air heat exchanger that absorbs heat from peripheral atmosphere.
13. a utmost point low-temperature freezing facilities, this cryogenic refrigerator comprise any one the described refrigerating circulatory device in the claim 1～9, it is characterized in that:
It comprises refrigerating chamber;
Above-mentioned the 1st heat exchanger is exothermic radiator; With
Above-mentioned the 2nd heat exchanger is the regenerator to cooling off in the above-mentioned refrigerating chamber.
CNB03136067XA 2002-04-04 2003-04-04 Refrigerating circulation apparatus Expired - Fee Related CN1220012C (en)

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